CN215260655U - Air return heat exchange tube set and refrigeration equipment - Google Patents

Abstract

The utility model relates to a refrigeration plant technical field provides a return air heat transfer tube group and refrigeration plant. The air return heat exchange tube group comprises an air return heat exchange tube body, and an air return tube, a capillary tube and a pressure relief tube are arranged inside the air return heat exchange tube body; the first end of the air return pipe is suitable for being connected to the outlet of the evaporator, and the second end of the air return pipe is suitable for being connected to the air inlet of the compressor; the first end of the capillary tube is suitable for being connected to the evaporator, and a pressure retaining valve is connected between the second end of the capillary tube and the condenser; a first end of the pressure relief tube is connected to the first end of the capillary tube and a second end of the pressure relief tube is adapted to be connected to an exhaust of the compressor. The air return heat exchange tube set can reduce the energy consumption of a refrigeration system, improve the refrigeration capacity and the refrigeration efficiency, and also can improve the defrosting efficiency of an evaporator.

Description

Air return heat exchange tube set and refrigeration equipment

Technical Field

The utility model relates to a refrigeration plant technical field especially relates to an air return heat exchange tube group and refrigeration plant.

Background

As shown in fig. 1, the refrigerant cycle process of the refrigeration system of the refrigerator is as follows: compression device 10 → exhaust evaporation tube → condensation device → anti-condensation tube → filter → capillary tube 30 → evaporation device 40 → return air heat exchange tube → compression device 10. The refrigerator belongs to intermittent refrigeration equipment, and after a compression device 10 is started up each time, a system needs to run for increasing the pressure of a condensing device and establishing a pressure difference with an evaporation device 40, a refrigerant flowing into the evaporation device 40 is evaporated to achieve a refrigeration effect.

After the compressor 10 is stopped, the refrigerant in the condenser is released, so that the pressure in the condenser in the refrigeration circuit is quickly restored to a low pressure state. When the compression device 10 is restarted, the system pressurization is carried out for a period of time again, and the pressure difference is reestablished, wherein the power of the compression device 10 is high, the external refrigeration cannot be normally carried out, and the electric energy is wasted.

And, when the refrigerating cycle is stopped, the high temperature refrigerant in the condensing unit flows into the evaporating unit 40 to raise the evaporating unit 40 to be higher than the freezing chamber temperature. That is, when the system is started, the system does not refrigerate for a period of time, but the temperature of the freezing chamber is increased, and the temperature of the evaporation device 40 is also increased, so that the starting power of the refrigerator is high, and the energy consumption is increased.

In addition, when the refrigeration cycle is stopped, the liquid refrigerant is vaporized due to the pressure reduction of the condensing device, so that the liquid refrigerant flowing into the evaporating device 40 after starting is reduced, the evaporating capacity is weakened, and the refrigerating capacity of the refrigerator is poor; meanwhile, as the refrigerant in the condensing device is vaporized, heat can be absorbed from the outside and transferred into the refrigerator through the evaporating device 40, which is contrary to the basic requirement of refrigeration of the refrigerator.

SUMMERY OF THE UTILITY MODEL

The utility model discloses aim at solving one of the technical problem that exists among the prior art at least. Therefore, the utility model provides an air return heat exchange tube group can reduce refrigerating system's energy consumption effectively, can also guarantee refrigerating system's refrigeration efficiency.

The utility model discloses still provide a refrigeration plant.

According to the utility model discloses return-air heat exchange tube group of first aspect embodiment includes:

the air return heat exchange tube body is internally provided with an air return tube, a capillary tube and a pressure relief tube;

the first end of the air return pipe is suitable for being connected to the outlet of the evaporator, and the second end of the air return pipe is suitable for being connected to the air inlet of the compressor;

the first end of the capillary tube is suitable for being connected to an evaporator, and a pressure retaining valve is connected between the second end of the capillary tube and the condenser;

the first end of the pressure relief tube is connected to the first end of the capillary tube, and the second end of the pressure relief tube is adapted to be connected to an exhaust port of a compressor.

According to the utility model discloses return-air heat exchange tube group of first aspect embodiment when needs make its operation refrigeration cycle, can make compressor exhaust refrigerant flow through condenser, pressure retaining valve, capillary and evaporimeter, flows back to the refrigerant circulation loop who forms complete refrigerating condition in the compressor at last. After the compressor is stopped, the compressor and the condenser are disconnected at the moment, and the pressure retaining valve is cut off, so that the high-temperature and high-pressure refrigerant on the high-pressure side does not flow to the evaporator and the air return heat exchange tube set any more, the refrigerant on the high-pressure side can maintain a high-temperature and high-pressure state, and the refrigerant on the low-pressure side can maintain a low-temperature and low-pressure state. Meanwhile, the pressure of the exhaust port of the compressor is released through the pressure release pipe, so that the pressure of the exhaust side and the pressure of the air inlet side of the compressor are balanced, the compressor can be normally started when being started next time, and the shutdown and pressure maintaining are realized. The air return heat exchange tube set can maintain the high pressure state of the condenser and the low pressure state of the evaporator during shutdown, so that the normal refrigeration working condition can be immediately entered without reestablishing pressure difference during restarting, and the energy consumption is reduced. After the evaporator frosts, the compressor and the condenser are disconnected and the pressure retaining valve is cut off, so that a refrigerant output by an exhaust port of the compressor can flow through the pressure relief pipe and the evaporator, the evaporator is directly heated, and then flows through the air return pipe to return to the compressor, and the evaporator is defrosted. The exhaust and defrosting design of the air return heat exchange tube set can be realized without using a heating tube, so that the space can be saved, the large-scale evaporator can be realized, and the refrigerating capacity of the refrigerating equipment can be improved.

According to the utility model discloses an embodiment, be connected with the three-way valve between the gas vent of the second end of pressure release pipe and compressor, the import of three-way valve is suitable for the gas vent that is connected to the compressor, an export of three-way valve is suitable for the import that is connected to the condenser in order to form the refrigeration circuit, another export of three-way valve with the second end intercommunication of pressure release pipe is in order to form the defrosting return circuit.

According to an embodiment of the present invention, a first end of the air return pipe is communicated with an outlet of the evaporator through a first pipeline, and a second end of the air return pipe is communicated with an air inlet of the compressor through a second pipeline;

the first end of the pressure relief pipe and the first end of the capillary are communicated with an inlet of the evaporator through a third pipeline;

the second end of the pressure relief pipe is communicated with an outlet of the three-way valve through a fourth pipeline;

and the second end of the capillary tube is communicated with the condenser through a fifth pipeline.

According to an embodiment of the present invention, the range of the cross-sectional area ratio of the air return pipe and the pressure release pipe is 2:1 to 4: 1.

According to the utility model discloses an embodiment, the value range of the external diameter of capillary is 1.5 millimeters to 2.5 millimeters, the value range of the internal diameter of capillary is 0.5 millimeters to 0.8 millimeters.

According to an embodiment of the present invention, a partition is disposed inside the air-return heat exchange tube body, the air-return tube and the pressure relief tube are partitioned by the partition, and the capillary tube is formed inside the partition along the length direction of the partition;

the thickness of the separator ranges from 0.5 mm to 1 mm.

According to the utility model discloses an embodiment, return air heat exchange tube body integrated into one piece, just return air heat exchange tube body is copper return air heat exchange tube body or aluminium system return air heat exchange tube body.

According to the utility model discloses an embodiment, the muffler the pressure release pipe and capillary respectively integrated into one piece, the capillary clamp is located the muffler with between the pressure release pipe.

An embodiment of the second aspect of the present invention provides a refrigeration device, including the above-mentioned air-return heat exchange tube set.

According to the utility model discloses refrigeration plant of second aspect embodiment, through using foretell return air heat transfer tube group, can make refrigeration plant when shutting down, the condenser also can maintain the high temperature state and dispel the heat outward, the evaporimeter can maintain the state that is less than the temperature in the refrigerator and refrigerate internally, guaranteed that the condenser is in highly compressed state, make it can not because of pressure drop liquid refrigerant evaporation vaporization, the liquid refrigerant that gets into the evaporimeter after guaranteeing to start is more, the evaporation capacity is stronger, make refrigeration plant's refrigerating capacity grow. Meanwhile, because the evaporator can be defrosted by the high-temperature refrigerant of the compressor, a heating pipe is not needed, the space is saved, the evaporator can be enlarged, the refrigerating capacity of the refrigerator is improved, and the energy consumption of refrigerating equipment is reduced. That is, the evaporator has more flexible design of the external dimension and installation position and mode because the heating pipe is not fixed.

According to an embodiment of the utility model, refrigeration plant is refrigerator, freezer or gradevin.

The embodiment of the utility model provides an in above-mentioned one or more technical scheme, one of following technological effect has at least:

according to the utility model discloses return-air heat exchange tube group of first aspect embodiment when needs make its operation refrigeration cycle, can make compressor exhaust refrigerant flow through condenser, pressure retaining valve, capillary and evaporimeter, flows back to the refrigerant circulation loop who forms complete refrigerating condition in the compressor at last. After the compressor is stopped, the compressor and the condenser are disconnected at the moment, and the pressure retaining valve is cut off, so that the high-temperature and high-pressure refrigerant on the high-pressure side does not flow to the evaporator and the air return heat exchange tube set any more, the refrigerant on the high-pressure side can maintain a high-temperature and high-pressure state, and the refrigerant on the low-pressure side can maintain a low-temperature and low-pressure state. Meanwhile, the pressure of the exhaust port of the compressor is released through the pressure release pipe, so that the pressure of the exhaust side and the pressure of the air inlet side of the compressor are balanced, the compressor can be normally started when being started next time, and the shutdown and pressure maintaining are realized. The air return heat exchange tube set can maintain the high pressure state of the condenser and the low pressure state of the evaporator during shutdown, so that the normal refrigeration working condition can be immediately entered without reestablishing pressure difference during restarting, and the energy consumption is reduced. After the evaporator frosts, the compressor and the condenser are disconnected and the pressure retaining valve is cut off, so that a refrigerant output by an exhaust port of the compressor can flow through the pressure relief pipe and the evaporator, the evaporator is directly heated, and then flows through the air return pipe to return to the compressor, and the evaporator is defrosted. The exhaust and defrosting design of the air return heat exchange tube set can be realized without using a heating tube, so that the space can be saved, the large-scale evaporator can be realized, and the refrigerating capacity of the refrigerating equipment can be improved.

Further, the utility model discloses the refrigeration plant that the embodiment of the second aspect provided, through using foretell return air heat transfer tube group, can make refrigeration plant when shutting down, the condenser also can maintain the high temperature state and dispel the heat outward, the evaporimeter can maintain the state that is less than the temperature in the refrigerator is internal to be refrigerated, guaranteed that the condenser is in highly compressed state, make it can not because of pressure drop liquid refrigerant evaporation vaporization, the liquid refrigerant that gets into the evaporimeter after guaranteeing to start is more, the evaporation capacity is stronger, make refrigeration plant's refrigerating capacity grow. Meanwhile, because the evaporator can be defrosted by the high-temperature refrigerant of the compressor, a heating pipe is not needed, the space is saved, the evaporator can be enlarged, the refrigerating capacity of the refrigerator is improved, and the energy consumption of refrigerating equipment is reduced. That is, the evaporator has more flexible design of the external dimension and installation position and mode because the heating pipe is not fixed.

Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.

FIG. 1 is a schematic block diagram of a prior art refrigeration unit;

fig. 2 is a schematic structural diagram of a refrigeration device provided by an embodiment of the present invention;

fig. 3 is a schematic perspective view of an air-return heat exchange tube body provided in an embodiment of the present invention;

fig. 4 is a schematic side view of an air return heat exchange tube body according to an embodiment of the present invention;

FIG. 5 is an enlarged view of a portion of FIG. 4 at A;

FIG. 6 is a partial enlarged view at B in FIG. 4;

fig. 7 is a schematic side view of another return air heat exchange tube body provided by an embodiment of the present invention;

FIG. 8 is an enlarged view of a portion of FIG. 7 at C;

fig. 9 is a schematic cross-sectional view of an air-return heat exchange tube body according to an embodiment of the present invention;

fig. 10 is a schematic cross-sectional view of another air-return heat exchange tube body provided in an embodiment of the present invention.

Reference numerals:

10. a compression device; 20. a condensing unit; 30. a capillary tube; 40. an evaporation device;

100. an air-return heat exchange tube body; 102. an air return pipe; 104. a capillary tube; 106. a pressure relief pipe; 108. an evaporator; 110. a compressor; 112. a condenser; 114. a pressure retaining valve; 116. a three-way valve; 118. a partition plate; 120. a first pipeline; 122. a second pipeline; 124. a third pipeline; 126. a fourth pipeline; 128. a fifth pipeline; 130. a condensation prevention pipe; 132. and drying the filter.

Detailed Description

The following describes embodiments of the present invention in further detail with reference to the accompanying drawings and examples. The following examples are intended to illustrate the invention, but are not intended to limit the scope of the invention.

In the description of the embodiments of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of describing the embodiments of the present invention and simplifying the description, but do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the embodiments of 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.

In the description of the embodiments of the present invention, it should be noted that, unless explicitly stated or limited otherwise, the terms "connected" and "connected" should be interpreted broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; may be directly connected or indirectly connected through an intermediate. The specific meaning of the above terms in the embodiments of the present invention can be understood in specific cases by those skilled in the art.

In embodiments of the invention, unless expressly stated or limited otherwise, the first feature may be directly on or directly under the second feature or indirectly via intermediate members. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of an embodiment of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

As shown in fig. 2 to 10, a first aspect of the present invention provides an air-return heat exchange tube set, including an air-return heat exchange tube body 100, where an air-return tube 102, a capillary tube 104, and a pressure relief tube 106 are arranged inside the air-return heat exchange tube body 100; a first end of the muffler 102 communicates with an outlet of the evaporator 108, and a second end of the muffler 102 communicates with an air inlet of the compressor 110; a first end of the capillary tube 104 is communicated with the evaporator 108, and a pressure retaining valve 114 is connected between a second end of the capillary tube 104 and the condenser 112; a first end of the pressure relief pipe 106 is connected to a first end of the capillary 104, a second end of the pressure relief pipe 106 is communicated with an exhaust port of the compressor 110, and a three-way valve 116 is connected between the second end of the pressure relief pipe 106 and the exhaust port of the compressor 110.

The utility model discloses the return-air heat exchange tube group that the embodiment of the first aspect provided when needs make its operation refrigeration cycle, can make compressor 110 exhaust refrigerant flow through three-way valve 116, condenser 112, pressure retaining valve 114, capillary 104 and evaporimeter 108, flow back to the refrigerant circulation loop that forms complete refrigerating condition in the compressor 110 at last.

When the compressor 110 is stopped, the three-way valve 116 adjusts the flow direction of the passage and the pressure retaining valve 114 is cut off, so that the high-temperature and high-pressure refrigerant on the high-pressure side does not flow to the evaporator 108 and the air-return heat exchange tube set any more, and thus the refrigerant on the high-pressure side can maintain the high-temperature and high-pressure state, and the refrigerant on the low-pressure side can maintain the low-temperature and low-pressure state. Meanwhile, the pressure of the exhaust port of the compressor 110 is relieved through the pressure relief pipe 106, so that the pressure on the exhaust side and the pressure on the air inlet side of the compressor 110 are balanced, the compressor 110 can be normally started when being started next time, and the shutdown and pressure maintaining are realized. Because the air-returning heat exchange tube group can maintain the high-pressure state of the condenser 112 and the low-pressure state of the evaporator 108 when the machine is stopped, the normal refrigeration working condition can be immediately entered without reestablishing the pressure difference when the machine is restarted, and the energy consumption is reduced.

When the evaporator 108 is frosted, the three-way valve 116 adjusts the flow direction of the passage again and the pressure retaining valve 114 is cut off, so that the refrigerant output from the exhaust port of the compressor 110 can flow through the pressure relief pipe 106 and the evaporator 108, directly heat the evaporator 108, and then flow through the air return pipe 102 to return to the compressor 110, thereby defrosting the evaporator 108. The exhaust and defrosting design of the air return heat exchange tube set can save space without using a heating tube, can realize the large-scale of the evaporator 108, and further can improve the refrigerating capacity of the refrigerating equipment.

In particular, the air-return heat exchange tube set provided by the embodiment of the first aspect of the present invention is applied to a refrigerator as an example.

The utility model discloses in the return-air heat exchange tube group that the embodiment of first aspect provided, mainly constitute by return-air heat exchange tube body 100, three-way valve 116 and pressure retaining valve 114.

Wherein, be provided with three kinds of different bodys in the inside of return air heat exchange tube body 100: a return pipe 102 for introducing a refrigerant into the compressor 110, a pressure relief pipe 106 for relieving pressure of the compressor 110, and a capillary tube 104 for throttling and depressurizing, respectively.

In the embodiment of the present invention, the air-return heat exchange tube body 100 can have at least the following two formation modes:

the forming method is as follows:

referring to fig. 3 to 6, the return air heat exchange tube body 100 is formed by integral molding, that is, in this forming manner, all three of the return air tube 102, the pressure relief tube 106 and the capillary tube 104 can be directly molded into an integral structure by extrusion or casting.

For example, the circular tube can be directly extruded by an extruder to form the corresponding air return tube 102, pressure relief tube 106, and capillary 104; alternatively, the mold may be opened in advance, and then the return pipe 102, the pressure relief pipe 106, and the capillary 104 may be directly cast by casting.

Thus, the air-return heat exchange tube body 100 formed in the above manner may be a copper air-return heat exchange tube body 100 or an aluminum air-return heat exchange tube body 100.

Of course, in other alternative embodiments, other materials may be used to form the return air heat exchange tube body 100, and are not exhaustive.

Referring to fig. 9, the cross section of the air-return heat exchange tube body 100 manufactured by the forming manner is hollow and circular, and an air return tube 102, a pressure relief tube 106 and a capillary tube 104 are formed inside the air-return heat exchange tube body.

That is, as shown in fig. 9, a partition 118 is provided inside the return heat exchange tube body 100, the partition 118 being provided along the length direction of the return heat exchange tube body 100.

In the embodiment of the present invention, the partition 118 functions to divide the internal space of the return air heat exchange tube body 100 into two parts, wherein one part of the space is used to form the return air tube 102 and the other part of the space is used to form the pressure relief tube 106; the second aspect of the partition 118 functions to enhance the structural strength of the return air heat exchange tube body 100 itself.

According to the utility model discloses an embodiment, in this kind of forming mode, because return air heat exchange tube body 100 forms through integrated into one piece's mode, consequently, capillary 104's the mode of setting is offered in the inside of baffle 118 for the length direction along baffle 118 in the embodiment of the utility model provides an, the value range of the thickness of baffle 118 is 0.5 millimeter to 1 millimeter. Of course, the thickness of the partition 118 ranges from 0.5 mm to 1 mm, and the outer diameter of the capillary 104 is not limited to 0.5 mm to 1 mm, and the outer diameter of the capillary 104 can be set to a desired size in order to meet the actual refrigeration requirement of the refrigerator.

The second forming method:

referring to fig. 7 and 8 in combination, in this forming mode, the muffler 102, the pressure relief pipe 106 and the capillary 104 are formed by integral molding, and the capillary 104 is sandwiched between the muffler 102 and the pressure relief pipe 106.

As shown in fig. 7 and 8, in one embodiment, there is no direct connection between the muffler 102 and the pressure relief tube 106 and the capillary 104, and a first end of the pressure relief tube 106 may be directly inserted into the capillary 104, and a second end of the pressure relief tube 106 is disposed parallel to the muffler 102 and the capillary 104.

Referring to fig. 10, in another embodiment, the air return tube 102, the pressure relief tube 106 and the capillary tube 104 may be formed by integral molding. The cross section of the air return pipe 102 and the cross section of the pressure relief pipe 106 are substantially D-shaped hollow pipe structures, and the cross section of the capillary 104 is a circular hollow pipe structure. In order to make the capillary 104 better fit with the muffler 102 and the pressure relief tube 106, a receiving groove for receiving the capillary 104 is provided in the muffler 102 along the longitudinal direction thereof; correspondingly, a receiving groove for receiving the capillary 104 is also provided in the pressure relief tube 106 along its length. After the muffler 102 and the pressure relief pipe 106 are attached to each other, the accommodating groove formed in the muffler 102 and the accommodating groove formed in the pressure relief pipe 106 can be spliced to form an accommodating space attached to the outer diameter of the capillary 104.

In addition, in order to ensure the bonding stability between the air return pipe 102, the pressure relief pipe 106, and the capillary 104, the air return pipe 102, the pressure relief pipe 106, and the capillary 104 may be connected by bonding, clamping, or the like. Both ends of the muffler 102 and the pressure release pipe 106 are not flattened, and a D-shaped hollow pipe structure is retained.

With continued reference to fig. 9 and 10, in the embodiment of the present invention, the ratio of the cross-sectional area of the air return pipe 102 to the cross-sectional area of the pressure relief pipe 106 ranges from 2:1 to 4: 1. That is, the diameter of the muffler 102 is approximately equal to 1.41 to 2 times the diameter of the pressure relief tube 106.

The smaller the diameter of the capillary 104, the longer the length, the smaller the flow rate of the refrigerant passing therethrough, and the lower the pressure; the larger the diameter and the shorter the length of the capillary tube 104, the more the flow rate and the higher the pressure of the refrigerant passing therethrough. According to the thermodynamic property of the refrigerant, the lower the pressure is, the lower the corresponding temperature is; the higher the pressure, the higher the corresponding temperature.

According to this law, if the diameter of the capillary tube 104 is too small or too long, the lower the pressure and temperature at the end of the capillary tube 104, and the corresponding lower the evaporation pressure and temperature. However, the decrease of the flow rate entering the evaporator 108 causes the evaporation speed to be reduced, the cooling capacity per unit time is reduced, and the cooling efficiency is affected.

If the tube diameter of the capillary tube 104 is too large or the length is too short, the higher the pressure and temperature at the end of the capillary tube 104, and the corresponding higher the vaporization pressure and temperature. The flow and pressure into the evaporator 108 will increase, which, although it will improve the evaporation efficiency, will result in an increase in the evaporation temperature and also in a poor cooling effect.

Therefore, in order to satisfy this structural characteristic of the capillary 104, in the embodiment of the present invention, the outer diameter of the capillary 104 may be set to 1.5 mm to 2.5 mm, and the inner diameter of the capillary 104 may be set to 0.5 mm to 0.8 mm. Therefore, the capillary tube 104 can meet the requirement of the refrigerant for low temperature and meet the requirement of evaporation efficiency at the same time.

In addition, it is also possible to prevent the freezing of the pipeline by providing a condensation preventing pipe 130 between the capillary tube and the condenser and providing a dry filter 132 on the condensation preventing pipe.

Referring to fig. 2, as mentioned above, the air-return heat exchange tube set provided in the embodiment of the first aspect of the present invention further includes a three-way valve 116, and the three-way valve 116 is connected between the second end of the pressure relief pipe 106 and the air outlet of the compressor 110. The three-way valve 116 is a one-in two-out valve, an inlet of the three-way valve 116 is communicated with an exhaust port of the compressor 110, an outlet of the three-way valve 116 is communicated with an inlet of the condenser 112 to form a normal refrigeration circuit, and another outlet of the three-way valve 116 is communicated with a second end of the pressure relief pipe 106 to form a defrosting circuit. At the same time, only one of the two outlets of the three-way valve 116 can be in communication with the inlet of the three-way valve 116. In other words, at the same time, the exhaust of the compressor 110 can only communicate with the inlet of the condenser 112 or the second end of the pressure relief tube 106.

With continued reference to fig. 2, as mentioned above, the air-return heat exchange tube set provided in the embodiment of the first aspect of the present invention further includes a pressure retaining valve 114, and the pressure retaining valve 114 is connected between the second end of the capillary tube 104 and the condenser 112. The pressure retaining valve 114 is an inlet valve and an outlet valve for intercepting the refrigerant between the condenser 112 and the evaporator 108.

The function of the three-way valve 116 and the pressure retaining valve 114 will be explained below in conjunction with the different states of the three-way valve 116 and the pressure retaining valve 114.

The utility model discloses the return-air heat exchange tube group that the embodiment of the first aspect provided can be applied to the operating mode demand of following three kinds of differences at least respectively:

the working condition requirement is as follows:

when the refrigerator needs to refrigerate, the compressor 110 is started, an outlet of the three-way valve 116, which is communicated with the condenser 112, is communicated with an inlet of the three-way valve 116, and at this time, the refrigerant discharged by the compressor 110 flows through the three-way valve 116, the condenser 112, the pressure retaining valve 114, the capillary tube 104 and the evaporator 108 in sequence, and finally flows back to the compressor 110 to form a complete refrigerant circulation loop in a refrigerating state.

The working condition requirement is two:

after the compressor 110 is stopped, in order to ensure that the compressor 110 is restarted, the problem that the refrigerator cannot refrigerate due to the fact that pressure difference does not need to be reestablished between the two sides of the compressor 110 is generated, an outlet of the three-way valve 116, which is communicated with the evaporator 108, is communicated with an inlet of the three-way valve 116, and meanwhile, the pressure retaining valve 114 is in a cut-off state, so that high-temperature and high-pressure refrigerant on a high-pressure side does not flow to the evaporator 108 and the air-return heat exchange tube set any more, and therefore the refrigerant on the high-pressure side can maintain a high-temperature and high-pressure state, and the refrigerant on a low-pressure side can maintain a low-temperature and low-pressure state. Meanwhile, the pressure of the exhaust port of the compressor 110 is relieved through the pressure relief pipe 106, so that the pressure on the exhaust side and the pressure on the air inlet side of the compressor 110 are balanced, and the shutdown and pressure maintaining can be realized.

The working condition requirement is three:

when the refrigerator operates for a certain period of time, because the temperature of the evaporator 108 is low, the surface of the evaporator 108 may frost after the refrigerator operates for a certain period of time. If the frost on the surface of the evaporator 108 is not removed in time, the frost layer becomes thicker and thicker, and the heat exchange efficiency of the evaporator 108 is affected when the frost layer reaches a certain thickness, so that the refrigerating capacity of the refrigerator is greatly reduced or even the refrigerator is not refrigerated.

Aiming at common direct-cooling refrigerators and air-cooling refrigerators, the direct-cooling refrigerators usually adopt an electric auxiliary heating wire for defrosting, and the defrosting method has the problems of large power consumption, incomplete defrosting, excessive compartment temperature return and the like.

The air-cooled refrigerator generally adopts a heating wire to carry out power-on heating defrosting, a heating pipe used in the defrosting mode is strong current, the safety risk of an electric appliance exists, meanwhile, a strong current load is added to the refrigerator, the circuit of the refrigerator is more complex, and the cost of a wire harness and a main control board is increased. In addition, the defrosting mode of strong heating enables the temperature of the heating pipe to be very high and can reach two to three hundred ℃, and the refrigerator liner and the air duct cover plate near the heating pipe are easily burnt and burnt. Meanwhile, the heating mode is slow in speed, long in defrosting time, and in the defrosting heating process, air, a box container, an air channel and the like near the evaporator 108 are heated, so that a large amount of heat is wasted. Since the heating pipe is fixed, the outer size and the installation position design of the evaporator 108 are limited, and the heating pipe occupies a certain space, the evaporator 108 cannot be made large.

Therefore, after the evaporator 108 is frosted, an outlet of the three-way valve 116, which is communicated with the evaporator 108, is communicated with an inlet of the three-way valve 116, so that a high-temperature refrigerant output by an exhaust port of the compressor 110 can directly enter the evaporator 108 through the pressure relief pipe 106, and further, the high-temperature refrigerant at the exhaust port of the compressor 110 can directly heat the evaporator 108 and then flows back to the compressor 110 through the air return pipe 102, thereby defrosting the evaporator 108.

According to an embodiment of the present invention, a first end of the muffler 102 communicates with an outlet of the evaporator 108 through a first pipe 120, and a second end of the muffler 102 communicates with an air inlet of the compressor 110 through a second pipe 122.

With reference to fig. 2 to 6, the first end of the muffler 102 is communicated with the outlet of the evaporator 108 through a first pipe 120, and the first pipe 120 may be fixed to the first end of the muffler 102 and the outlet of the evaporator 108 by welding.

The second end of the muffler 102 is communicated with the air inlet of the compressor 110 through a second pipeline 122, and the second pipeline 122 may be respectively communicated with the second end of the muffler 102 and the air inlet of the compressor 110 through welding.

It will be appreciated that the first and second ends of the return air pipe 102 are connected to the first and second pipes 120 and 122, respectively, so that the return air pipe 102 is in communication with the outlet of the evaporator 108 and the inlet of the compressor 110, respectively. Of course, in other embodiments, the first end of the air return pipe 102 can be connected to the outlet of the evaporator 108 and the second end of the air return pipe 102 can be connected to the air inlet of the compressor 110 by means of plugging, clamping, and the like. Alternatively, both ends of the return air pipe 102 may be directly connected to the outlet of the evaporator 108 and the air inlet of the compressor 110.

A first end of the pressure relief tube 106 and a first end of the capillary tube 104 are in communication with an inlet of the evaporator 108 via a third line 124; a second end of the pressure relief tube 106 communicates with an outlet of the three-way valve 116 via a fourth line 126; the second end of the capillary tube 104 communicates with the condenser 112 through a fifth line 128.

The first end of the capillary tube 104 is connected to the inlet of the evaporator 108 via the third pipeline 124. As mentioned above, the first end of the pressure relief tube 106 is connected between the capillary tube 104 and the inlet of the evaporator 108, and thus the first end of the pressure relief tube 106 is also connected to the inlet of the evaporator 108 via the third pipeline 124.

In other words, the first end of the capillary tube 104 and the first end of the pressure relief tube 106 may be welded to the first end of the third tube 124 at the same time, and the second end of the third tube 124 may be welded directly to the inlet of the evaporator 108.

The second end of the pressure relief pipe 106 and one of the outlets of the three-way valve 116 may be connected by a fourth pipeline 126, and two ends of the fourth pipeline 126 may be connected to the second end of the pressure relief pipe 106 and one of the outlets of the three-way valve 116 by welding, plugging, clamping, and the like.

The second end of the capillary tube 104 is connected to the condenser 112 through a fifth pipe 128, for example, two ends of the fifth pipe 128 may be respectively connected to the second end of the capillary tube 104 and the condenser 112 by welding, plugging, clamping, etc.

Of course, in other embodiments, the first end of the capillary tube 104 and the first end of the pressure relief tube 106 may be directly connected to the inlet of the evaporator 108, the second end of the capillary tube 104 may be directly connected to the condenser 112, and the second end of the pressure relief tube 106 may be directly connected to one of the outlets of the three-way valve 116.

The air return heat exchange tube set provided by the embodiment of the first aspect of the present invention is described below with reference to fig. 2 to 6:

first, a pressure retaining valve 114 is provided between the second end of the capillary tube 104 and the condenser 112, and a three-way valve 116 is connected between the discharge port of the compressor 110 and the condenser 112;

then, a first end of the return air pipe 102 in the return air heat exchange pipe body 100 is connected to an outlet of the evaporator 108 through a first pipe 120, and a second end of the return air pipe 102 is connected to an air inlet of the compressor 110 through a second pipe 122; a first end of the capillary tube 104 and a first end of the pressure relief tube 106 in the return air heat exchange tube body 100 are connected to an inlet of the evaporator 108 through a third pipeline 124, a second end of the pressure relief tube 106 is connected to an outlet of the three-way valve 116 through a fourth pipeline 126, and a second end of the capillary tube 104 is connected to the condenser 112 through a fifth pipeline 128;

when refrigeration is needed, an outlet of the three-way valve 116, which is communicated with the condenser 112, is communicated with an inlet of the three-way valve 116, and at the moment, a refrigerant discharged by the compressor 110 sequentially flows through the three-way valve 116, the condenser 112, the pressure retaining valve 114, the capillary tube 104 and the evaporator 108, and finally flows back to the compressor 110 to form a complete refrigerant circulation loop in a refrigeration state;

when the compressor 110 is required to stop and maintain pressure, an outlet of the three-way valve 116, which is communicated with the evaporator 108, is communicated with an inlet of the three-way valve 116, and meanwhile, the pressure maintaining valve 114 is in a cut-off state; the high-temperature and high-pressure refrigerant on the high-pressure side no longer flows to the evaporator 108 and the air-return heat exchange tube set, so that the refrigerant on the high-pressure side can maintain a high-temperature and high-pressure state, and the refrigerant on the low-pressure side can maintain a low-temperature and low-pressure state. Meanwhile, the exhaust port of the compressor 110 is decompressed through the evaporator 108, so that the pressure on the exhaust side and the pressure on the air inlet side of the compressor 110 are balanced;

when the evaporator 108 needs to be defrosted, an outlet of the three-way valve 116, which is communicated with the evaporator 108, is communicated with an inlet of the three-way valve 116, so that the refrigerant output from an exhaust port of the compressor 110 can directly enter the evaporator 108 through the pressure relief pipe 106, and further, the high-temperature refrigerant at the exhaust port of the compressor 110 can directly heat the evaporator 108 and then flows back to the compressor 110 through the air return pipe 102, thereby defrosting the evaporator 108.

According to the utility model discloses the refrigeration plant that the embodiment of second aspect provided, including foretell return air heat transfer tube group.

The utility model discloses the refrigeration plant that the embodiment of the second aspect provided, through using foretell return air heat exchange tube group, can make refrigeration plant when shutting down, condenser 112 also can maintain the high temperature state and dispel the heat outward, evaporimeter 108 can maintain the state that is less than the temperature in the refrigerator and refrigerate internally, condenser 112 has been guaranteed to be in highly compressed state, make it can not because of the pressure drop liquid refrigerant evaporation vaporization, the liquid refrigerant that gets into evaporimeter 108 after guaranteeing to start is more, the evaporation capacity is stronger, make refrigeration plant's refrigerating capacity grow. Meanwhile, because the evaporator 108 can be defrosted by using the high-temperature refrigerant of the compressor 110, a heating pipe is not needed, the space is saved, the evaporator 108 can be enlarged, the refrigerating capacity of the refrigerator is improved, and the energy consumption of refrigerating equipment is reduced. That is, the evaporator 108 is more flexible in design of external dimensions and installation location and manner, since no fixed heating tube is used.

According to an embodiment of the utility model, the refrigeration plant is refrigerator, freezer or gradevin.

Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it should be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; such modifications and substitutions do not depart from the spirit and scope of the present invention in its corresponding aspects.

The above embodiments are merely illustrative, and not restrictive, of the present invention. Although the present invention has been described in detail with reference to the embodiments, it should be understood by those skilled in the art that various combinations, modifications or equivalent substitutions may be made to the technical solution of the present invention without departing from the spirit and scope of the technical solution of the present invention, and all of the technical solutions should be covered by the scope of the claims of the present invention.

Claims (10)

1. An air return heat exchange tube set, comprising:

the air return heat exchange tube comprises an air return heat exchange tube body (100), wherein an air return tube (102), a capillary tube (104) and a pressure relief tube (106) are arranged inside the air return heat exchange tube body (100);

a first end of the air return pipe (102) is suitable for being connected to an outlet of the evaporator (108), and a second end of the air return pipe (102) is suitable for being connected to an air inlet of the compressor (110);

the first end of the capillary tube (104) is suitable for being connected to an evaporator (108), and a pressure retaining valve (114) is connected between the second end of the capillary tube (104) and the condenser (112);

a first end of the pressure relief tube (106) is connected to a first end of the capillary tube (104), and a second end of the pressure relief tube (106) is adapted to be connected to an exhaust of a compressor (110).

2. The return air heat exchange tube set according to claim 1, characterized in that a three-way valve (116) is connected between the second end of the pressure relief tube (106) and the exhaust port of the compressor (110), an inlet of the three-way valve (116) is adapted to be connected to the exhaust port of the compressor (110), one outlet of the three-way valve (116) is adapted to be connected to an inlet of the condenser (112) to form a refrigeration circuit, and another outlet of the three-way valve (116) is communicated with the second end of the pressure relief tube (106) to form a defrost circuit.

3. The air return heat exchange tube set according to claim 2, wherein a first end of the air return tube (102) communicates with an outlet of the evaporator (108) through a first pipe (120), and a second end of the air return tube (102) communicates with an air inlet of the compressor (110) through a second pipe (122);

the first end of the pressure relief pipe (106) and the first end of the capillary (104) are communicated with an inlet of the evaporator (108) through a third pipeline (124);

a second end of the pressure relief pipe (106) is communicated with an outlet of the three-way valve (116) through a fourth pipeline (126);

the second end of the capillary tube (104) is in communication with the condenser (112) via a fifth conduit (128).

4. The air return heat exchange tube set according to claim 1, wherein the ratio of the cross-sectional areas of the air return tube (102) and the pressure relief tube (106) ranges from 2:1 to 4: 1.

5. The air return heat exchange tube set according to claim 4, wherein the outer diameter of the capillary tube (104) ranges from 1.5 mm to 2.5 mm, and the inner diameter of the capillary tube (104) ranges from 0.5 mm to 0.8 mm.

6. The air-return heat exchange tube set according to any one of claims 1 to 5, wherein a partition plate (118) is provided inside the air-return heat exchange tube body (100), the air-return tube (102) and the pressure relief tube (106) are partitioned by the partition plate (118), and the capillary tube (104) is formed inside the partition plate (118) along the length direction of the partition plate (118);

the thickness of the partition plate (118) ranges from 0.5 mm to 1 mm.

7. The air-return heat exchange tube set according to claim 6, wherein the air-return heat exchange tube body (100) is integrally formed, and the air-return heat exchange tube body (100) is a copper air-return heat exchange tube body (100) or an aluminum air-return heat exchange tube body (100).

8. The air return heat exchange tube set according to any one of claims 1 to 5, wherein the air return tube (102), the pressure relief tube (106), and the capillary tube (104) are respectively integrally molded, and the capillary tube (104) is sandwiched between the air return tube (102) and the pressure relief tube (106).

9. Refrigeration device, characterized in that it comprises a set of return air heat exchange tubes according to any one of claims 1 to 8.

10. A refrigeration device as recited in claim 9 wherein the refrigeration device is a refrigerator, freezer or wine chest.

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