CN117308415A - Heat exchange device for refrigerant circulation system and refrigerant circulation system - Google Patents

Abstract

The application relates to the technical field of air conditioning and discloses a heat exchange device for a refrigerant circulation system, wherein the heat exchange device for the refrigerant circulation system comprises a first pipe body and a second pipe body, and a refrigerant flowing space is defined in the first pipe body; the second pipe body is sleeved on the first pipe body, a throttling flow passage is formed between the first pipe body and the second pipe body, and the refrigerant flowing through the throttling flow passage exchanges heat with the refrigerant flowing through the refrigerant flowing space. The application also discloses a refrigerant circulation system.

Description

Heat exchange device for refrigerant circulation system and refrigerant circulation system

Technical Field

The present application relates to the field of air conditioning technologies, and for example, to a heat exchange device for a refrigerant circulation system and a refrigerant circulation system.

Background

In the refrigerant circulation system, the larger the supercooling degree of the liquid refrigerant flowing out of the condenser is, the better the flowing stability of the refrigerant is, and the better the refrigerating and heating effects of the refrigerant circulation system are. A supercooling pipe section is usually arranged at the tail section of the condenser so as to obtain a certain supercooling degree of the liquid refrigerant. This process is also referred to as primary subcooling. The length of the supercooling pipe section is increased due to the temperature difference between the liquid refrigerant in the supercooling pipe section and the environment, and the supercooling degree is improved only to a limited extent.

In order to further improve the supercooling degree of the liquid refrigerant, an air conditioner is disclosed in the related art, which comprises an auxiliary gas-liquid separator for separating the refrigerant flowing out of the outdoor heat exchanger and throttled into gas and liquid, a plate heat exchanger for secondary supercooling and an auxiliary electronic expansion valve, wherein a main flow path of the plate heat exchanger sends the liquid refrigerant into an indoor unit, and an auxiliary flow path sends the gas refrigerant throttled by the auxiliary electronic expansion valve into the outdoor unit. In the air conditioner in the related art, the temperature of the refrigerant in the main flow path is reduced through the evaporation and heat absorption of the refrigerant in the auxiliary flow path in the plate heat exchanger, so that the supercooling degree of the refrigerant in the main flow path is further improved.

In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in the related art:

when the refrigerant flows through the electronic expansion valve of the auxiliary flow path, heat is absorbed from the environment, and thus, the cooling capacity of the refrigerant circulation system is lost.

It should be noted that the information disclosed in the foregoing background section is only for enhancing understanding of the background of the present application and thus may include information that does not form the prior art that is already known to those of ordinary skill in the art.

Disclosure of Invention

The following presents a simplified summary in order to provide a basic understanding of some aspects of the disclosed embodiments. This summary is not an extensive overview, and is intended to neither identify key/critical elements nor delineate the scope of such embodiments, but is intended as a prelude to the more detailed description that follows.

The embodiment of the disclosure provides a heat exchange device for a refrigerant circulation system and the refrigerant circulation system so as to reduce the cooling capacity loss of the refrigerant circulation system.

In some embodiments, the heat exchange device for a refrigerant circulation system includes a first tube and a second tube, wherein an interior of the first tube defines a refrigerant flow space; the second pipe body is sleeved on the first pipe body, a throttling flow passage is formed between the first pipe body and the second pipe body, and the refrigerant flowing through the throttling flow passage exchanges heat with the refrigerant flowing through the refrigerant flowing space.

In some embodiments, the throttling channel is spiral, and the throttling channel is wound around the refrigerant flowing space.

In some embodiments, the heat exchange device further comprises a spiral member, an inward side of the spiral member abuts against an outer wall of the first tube, an outward side of the spiral member abuts against an inner wall of the second tube, and the spiral member defines the spiral throttling channel between the first tube and the second tube.

In some embodiments, the first pipe body is provided with a threaded groove towards the second pipe body, and an opening of the threaded groove is abutted against the inner wall of the second pipe body to form the spiral throttling flow passage.

In some embodiments, the second pipe body is configured with a threaded groove facing the first pipe body, and an opening of the threaded groove abuts against the outer wall of the first pipe body to form the spiral throttling flow passage.

In some embodiments, in a case where the first pipe body is configured with a screw groove toward the second pipe body, a side of the first pipe body toward the refrigerant flow space forms a screw protrusion corresponding to the screw groove.

In some embodiments, the heat exchange device further includes a main pipe, the interior defines a refrigerant flow channel, a heat exchange space is defined between the first pipe body and an outer wall of the main pipe, the refrigerant flow space includes the heat exchange space and the refrigerant flow channel, the refrigerant flowing through the throttle flow channel exchanges heat with the refrigerant flowing through the heat exchange space, and the refrigerant flowing through the heat exchange space exchanges heat with the refrigerant flowing through the refrigerant flow channel.

In some embodiments, in a case that a screw protrusion is formed on a surface of the first pipe body facing the refrigerant flowing space, the screw protrusion abuts against an outer wall of the main pipe to form a screw flow passage.

In some embodiments, the first pipe body is provided with a first interface, and the first end of the throttling flow passage is communicated with the heat exchange space through the first interface.

In some embodiments, the heat exchange device further comprises a connecting pipeline, one end of the connecting pipeline is communicated with the refrigerant flow passage of the main pipeline, the other end of the connecting pipeline is communicated with the second end of the throttling flow passage, and a part of liquid refrigerant flowing through the main pipeline enters the throttling flow passage through the connecting pipeline.

In some embodiments, the refrigerant circulation system includes a compressor, a condenser, a throttling device, an evaporator, and the heat exchange device described above, wherein a suction end of the compressor is connected to a discharge end of the throttling flow channel; the liquid outlet end of the condenser is communicated with a refrigerant inlet of the refrigerant flowing space, and the air inlet end of the condenser is communicated with exhaust gas of the compressor; the liquid inlet end of the throttling device is communicated with a refrigerant outlet of the refrigerant flowing space; the liquid inlet end of the evaporator is communicated with the liquid outlet end of the throttling device, and the gas outlet end of the evaporator is communicated with the gas suction end of the compressor.

The heat exchange device for the refrigerant circulation system and the refrigerant circulation system provided by the embodiment of the disclosure can realize the following technical effects:

the heat exchange device adopts a mode of sleeving a main pipeline by an outer pipe, has smaller volume, lower cost and flexible installation position; a part of refrigerant exchanges heat with the refrigerant in the main pipeline through the heat exchange space, and the refrigerant in the main pipeline can have larger supercooling degree, so that the refrigerating and heating effects of the refrigerant circulation system can be improved; a throttling flow channel is formed between the inner wall and the outer wall of the outer tube, the appearance of the heat exchange device is neat, and the throttling effect is stable; the refrigerant in the throttling flow passage indirectly exchanges heat with the liquid refrigerant in the main pipeline, and the liquid refrigerant in the main pipeline can obtain larger supercooling degree.

The foregoing general description and the following description are exemplary and explanatory only and are not restrictive of the application.

Drawings

One or more embodiments are illustrated by way of example and not limitation in the figures of the accompanying drawings, in which like references indicate similar elements, and in which like reference numerals refer to similar elements, and in which:

fig. 1 is a schematic structural diagram of a heat exchange device for a refrigerant circulation system according to an embodiment of the present disclosure;

FIG. 2 is a schematic view of another heat exchange device for a refrigerant circulation system according to an embodiment of the present disclosure;

FIG. 3 is a schematic view of another heat exchange device for a refrigerant circulation system according to an embodiment of the present disclosure;

FIG. 4 is a schematic view of another heat exchange device for a refrigerant circulation system according to an embodiment of the present disclosure;

FIG. 5 is a schematic cross-sectional view of a heat exchange device for a refrigerant circulation system according to an embodiment of the present disclosure;

fig. 6 is a schematic structural diagram of a refrigerant circulation system according to an embodiment of the disclosure.

Reference numerals:

100: an outer tube; 110: a first tube body; 111: a refrigerant flowing space; 120: a second tube body; 130: a throttle flow passage; 140: a screw; 200: a main pipeline; 201: a refrigerant flow passage; 202: a heat exchange space; 300: a connecting pipeline; 10: a heat exchange device; 20: a compressor; 21: an air suction port; 22: an air jet; 30: a condenser; 40: a throttle device; 50: an evaporator.

Detailed Description

So that the manner in which the features and techniques of the disclosed embodiments can be understood in more detail, a more particular description of the embodiments of the disclosure, briefly summarized below, may be had by reference to the appended drawings, which are not intended to be limiting of the embodiments of the disclosure. In the following description of the technology, for purposes of explanation, numerous details are set forth in order to provide a thorough understanding of the disclosed embodiments. However, one or more embodiments may still be practiced without these details. In other instances, well-known structures and devices may be shown simplified in order to simplify the drawing.

The terms first, second and the like in the description and in the claims of the embodiments of the disclosure and in the above-described figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It will be appreciated that the data so used may be interchanged where appropriate. Furthermore, the terms "comprise" and "have," as well as any variations thereof, are intended to cover a non-exclusive inclusion.

In the embodiments of the present disclosure, the terms "upper", "lower", "inner", "middle", "outer", "front", "rear", and the like indicate an azimuth or a positional relationship based on that shown in the drawings. These terms are used primarily to better describe embodiments of the present disclosure and embodiments thereof and are not intended to limit the indicated device, element, or component to a particular orientation or to be constructed and operated in a particular orientation. Also, some of the terms described above may be used to indicate other meanings in addition to orientation or positional relationships, for example, the term "upper" may also be used to indicate some sort of attachment or connection in some cases. The specific meaning of these terms in the embodiments of the present disclosure will be understood by those of ordinary skill in the art in view of the specific circumstances.

In addition, the terms "disposed," "connected," "secured" and "affixed" are to be construed broadly. For example, "connected" may be in a fixed connection, a removable connection, or a unitary construction; may be a mechanical connection, or an electrical connection; may be directly connected, or indirectly connected through intervening media, or may be in internal communication between two devices, elements, or components. The specific meaning of the above terms in the embodiments of the present disclosure may be understood by those of ordinary skill in the art according to specific circumstances.

The term "plurality" means two or more, unless otherwise indicated.

In the embodiment of the present disclosure, the character "/" indicates that the front and rear objects are an or relationship. For example, A/B represents: a or B.

The term "and/or" is an associative relationship that describes an object, meaning that there may be three relationships. For example, a and/or B, represent: a or B, or, A and B.

It should be noted that, without conflict, the embodiments of the present disclosure and features of the embodiments may be combined with each other.

In the refrigerant circulation system, the larger the supercooling degree of the liquid refrigerant flowing out of the condenser is, the better the flowing stability of the refrigerant is, and the better the refrigerating and heating effects of the refrigerant circulation system are. A supercooling pipe section is usually arranged at the tail section of the condenser so as to obtain a certain supercooling degree of the liquid refrigerant. This process is also referred to as primary subcooling. The length of the supercooling pipe section is increased due to the temperature difference between the liquid refrigerant in the supercooling pipe section and the environment, and the supercooling degree is improved only to a limited extent. In order to further improve the supercooling degree of the liquid refrigerant, an air conditioner is disclosed in the related art, which comprises an auxiliary gas-liquid separator for separating the refrigerant flowing out of the outdoor heat exchanger and throttled into gas and liquid, a plate heat exchanger for secondary supercooling and an auxiliary electronic expansion valve, wherein a main flow path of the plate heat exchanger sends the liquid refrigerant into an indoor unit, and an auxiliary flow path sends the gas refrigerant throttled by the auxiliary electronic expansion valve into the outdoor unit. In the air conditioner in the related art, the temperature of the refrigerant in the main flow path is reduced through the evaporation and heat absorption of the refrigerant in the auxiliary flow path in the plate heat exchanger, so that the supercooling degree of the refrigerant in the main flow path is further improved. The related art has a problem in that the refrigerant absorbs heat from the environment when flowing through the electronic expansion valve of the auxiliary flow path, which causes a loss of cooling capacity of the refrigerant circulation system.

In order to reduce the cooling capacity loss of the refrigerant circulation system, referring to fig. 1-4, an embodiment of the disclosure provides a heat exchange device for a refrigerant circulation system, the heat exchange device includes a first pipe body 110 and a second pipe body 120, wherein a refrigerant flowing space 111 is defined in the first pipe body 110; the second pipe body 120 is sleeved on the first pipe body 110, a throttling flow channel 130 is formed between the first pipe body 110 and the second pipe body 120, and the refrigerant flowing through the throttling flow channel 130 exchanges heat with the refrigerant flowing through the refrigerant flowing space 111.

In the disclosed embodiment, the heat exchange device includes an outer tube 100, the outer tube 100 including a first tube body 110 and a second tube body 120. The first tube 110 has a refrigerant flow space 111 in which a liquid refrigerant or a gaseous refrigerant flows.

A throttle duct 130 is formed in the wall of the outer tube 100, i.e., the throttle duct 130 is formed between the first tube body 110 and the second tube body 120. The throttle flow path 130 is used to provide throttle resistance, and to block the high and low pressure environments at both ends of the throttle flow path 130 in a state where both ends connected to the throttle flow path 130 are in communication. When the high-pressure liquid refrigerant flows through the throttle channel 130, the refrigerant evaporates into a gaseous state due to the pressure decrease, and absorbs heat during the evaporation.

Under the condition that the air conditioner operates in a refrigeration mode, heat absorption of the throttling component from the environment can cause an increase of enthalpy of a refrigerant in the refrigerant circulation system, namely, the heat loss of the refrigerant circulation system is caused. Therefore, the throttle flow path 130 is configured between the first pipe body 110 and the second pipe body 120, and the refrigerant absorbs heat from the refrigerant in the refrigerant flowing space 111 when the refrigerant evaporates in the throttle flow path 130. In this way, the temperature of the refrigerant flowing through the refrigerant flowing space 111 is reduced through the throttling channel 130, and the temperature of the liquid refrigerant is reduced after flowing through the refrigerant flowing space 111, so that a larger supercooling degree is obtained.

When the refrigerant flows through the throttling flow passage which plays a role in throttling, the refrigerant is mainly in a liquid state in the first section of the throttling flow passage, the flow speed is not greatly changed, and the pressure of the refrigerant is linearly reduced. The temperature difference between the refrigerant and the external environment of the throttling flow passage in the section is smaller, and the heat exchange is smaller. When the heat exchange refrigerant flows to the second section of the throttling flow passage, evaporation starts due to pressure reduction. The volume expansion flow velocity is increased after the refrigerant is evaporated, and the pressure drop of the refrigerant is larger at the section. The evaporation heat absorption of the cooling medium in the section is increased, and heat is absorbed from the environment where the throttling flow passage is located through the pipe wall of the throttling flow passage in the evaporation process. When the refrigerant flows to the end section of the second section of the throttling flow passage, the flow velocity of the gaseous refrigerant reaches the maximum, and the flow velocity cannot be further increased. The temperature of the evaporated refrigerant is lower, and the refrigerant continuously exchanges heat with the pipe wall wound by the throttling flow passage through the pipe wall of the throttling flow passage. Meanwhile, the wall of the throttling flow passage has certain heat conductivity, the temperature of the first section of the throttling flow passage is lower than the temperature of the appearance, and the refrigerant flowing through the first section of the throttling flow passage exchanges heat with the refrigerant in the outer tube. The throttling and the evaporation of the refrigerant are completed in a throttling flow passage, and the throttling flow passage equivalently plays roles of throttling and heat exchange.

With the arrangement, the throttle flow channel 130 is defined between the first pipe body 110 and the second pipe body 120, and the evaporation heat absorption of the refrigerant in the throttle flow channel 130 can be utilized, so that the cold energy loss of the refrigerant circulation system is reduced; the refrigerant absorbs heat in the throttling flow passage 130 by evaporation to reduce the temperature of the refrigerant flowing through the heat exchange space 202, and the refrigerant can obtain larger supercooling degree when the refrigerant is in a liquid state, so that the refrigerating and heating effects of the refrigerant circulation system are improved.

Alternatively, the throttle flow passage 130 is spiral, and the throttle flow passage 130 is wound around the refrigerant flow space 111.

The spiral throttling flow passage 130 can enhance the throttling and depressurization effects. For example, for the R134a refrigerant, under the same mass flow rate and the same pipe inner diameter, when the same throttling effect is achieved, the spiral throttling flow passage 130 is 14% shorter than the straight pipe throttling flow passage 130; with the same tube inside diameter and the same tube length, the mass flow rate of the spiral-type flow restriction 130 is about 1% less than that of the straight-tube-type flow restriction 130.

The throttling flow passage 130 is spiral, and can be provided with a longer length in a limited space, so that a larger heat exchange area is provided between the refrigerant in the throttling flow passage 130 and the refrigerant in the heat exchange space 202. In this way, the heat exchange effect between the refrigerant in the throttling channel 130 and the refrigerant in the heat exchange space 202 can be improved, so that the cooling effect on the refrigerant in the heat exchange tube is indirectly improved.

Optionally, the heat exchange device further includes a spiral member 140, an inward surface of the spiral member 140 abuts against an outer wall of the first tube body 110, an outward surface abuts against an inner wall of the second tube body 120, and the spiral member 140 defines a spiral throttling channel 130 between the first tube body 110 and the second tube body 120.

The axis of the screw 140 coincides with the axis of the first pipe body 110 and the second pipe body 120, and each turn of thread of the screw 140 is distributed along the axis of the screw 140 with a certain pitch, and the diameters of the space ring threads of the screw 140 are the same. The inner ring of the screw 140 abuts against the outer wall of the first pipe body 110, and the outer ring abuts against the inner wall of the second pipe body 120. A spiral flow path is formed between two adjacent turns of the screw 140. The threads of the screw 140 are continuously distributed and the screw flow channels are continuously distributed. With such an arrangement, the structure is simple and the cost is low, which is beneficial to the processing and assembly of the outer tube 100.

Illustratively, the screw 140 is a spring.

Optionally, the first pipe body 110 is configured with a threaded groove towards the second pipe body 120, and an opening of the threaded groove abuts against an inner wall of the second pipe body 120 to form a spiral throttling flow passage 130.

The first pipe body 110 is configured with a threaded groove towards the second pipe body 120, and an opening of the threaded groove is abutted against the inner wall of the second pipe body 120 and then enclosed with the inner wall of the second pipe body 120 to define a threaded throttling flow passage 130. With such an arrangement, the outer tube 100 is advantageously formed.

Optionally, the second pipe body 120 is configured with a threaded groove towards the first pipe body 110, and an opening of the threaded groove abuts against an inner wall of the first pipe body 110 to form a spiral throttling flow passage 130.

The second pipe body 120 is configured with a threaded groove towards the first pipe body 110, and an opening of the threaded groove is abutted against the outer wall of the first pipe body 110 and then enclosed with the outer wall of the second pipe body 120 to define a threaded throttling flow passage 130. With such an arrangement, the outer tube 100 is advantageously formed.

Optionally, the first tube 110 and the second tube 120 are each configured with a threaded groove, and the threaded groove of the first tube 110 and the threaded groove of the second tube 120 are butted to form a spiral throttling flow passage 130.

With such an arrangement, the flatness of the cross section of the throttle flow path 130 can be reduced, thereby reducing the risk of the throttle flow path 130 being blocked.

Alternatively, in case that the first pipe body 110 is configured with a screw groove toward the second pipe body 120, a side of the first pipe body 110 toward the refrigerant flowing space 111 forms a screw protrusion corresponding to the screw groove.

In the case that the first tube 110 is a single-layer tube, a threaded groove is formed on a surface of the first tube 110 facing the second tube 120, and a threaded protrusion is formed on a surface of the second tube 120 facing the heat exchange space 202. With such an arrangement, the resistance of the refrigerant flowing in the heat exchange space 202 can be increased, and the laminar boundary layer of the refrigerant flowing can be broken. This can further enhance the heat exchange effect between the refrigerant in the heat exchange space 202 and the refrigerant in the main pipe 200 and the refrigerant in the throttle channel 130.

Optionally, the heat exchange device further includes a main pipe 200, a refrigerant flow channel 201 is defined in the main pipe 200, a heat exchange space 202 is defined between the first pipe body 110 and an outer wall of the main pipe 200, the refrigerant flowing space 111 includes the heat exchange space 202 and the refrigerant flow channel 201, the refrigerant flowing through the throttling channel 130 exchanges heat with the refrigerant flowing through the heat exchange space 202, and the refrigerant flowing through the heat exchange space 202 exchanges heat with the refrigerant flowing through the refrigerant flow channel 201.

The heat exchange device includes a main pipe 200 and an outer pipe 100. The main pipe 200 is used for connecting two adjacent or related functional components in the refrigerant circulation system, and provides a refrigerant flow channel 201 for the flow of liquid refrigerant. The main line 200 is illustratively a length of refrigerant tubing connected between the condenser and the restriction. The two ends of the main pipeline 200 are respectively provided with a refrigerant inlet and a refrigerant outlet.

The outer tube 100 is sleeved on the main pipeline 200, and a heat exchange space 202 is defined between the inner wall of the outer tube 100 and the outer wall of the main pipeline 200. As an implementation form, after the outer tube 100 is sleeved on the main pipeline 200, two ends of the outer tube 100 are sealed with the outer wall of the main pipeline 200 by welding. A throttle flow passage 130 is defined between the inner and outer walls of the outer tube 100, and the throttle flow passage 130 can provide a certain throttle resistance to isolate high and low pressure environments in the refrigerant circulation system.

The refrigerant flowing to the main pipe 200 and the heat exchanging space 202 between the main pipe 200 and the first pipe body 110 are all part of the refrigerant flowing space 111. In the case that the heat exchange device is provided with the main pipe 200, the refrigerant in the main pipe 200 is used as a cooling object, and the refrigerant in the throttle flow passage 130 evaporates and absorbs heat to reduce the temperature of the refrigerant in the heat exchange space 202, thereby indirectly reducing the temperature of the refrigerant in the main pipe 200.

The heat exchange device adopts the mode that the outer pipe 100 is sleeved with the main pipeline 200, the volume is small, the cost is low, and the installation position is flexible; the refrigerant exchanges heat with the refrigerant in the main pipeline 200 through the heat exchange space 202, and the refrigerant in the main pipeline 200 can have larger supercooling degree, so that the refrigerating and heating effects of the refrigerant circulation system can be improved; a throttling flow passage 130 is formed between the inner wall and the outer wall of the outer tube 100, the appearance of the heat exchange device is neat, and the throttling effect is stable; the refrigerant in the throttling channel 130 indirectly exchanges heat with the liquid refrigerant in the pipeline, and the liquid refrigerant in the main pipeline 200 can obtain a larger supercooling degree.

Alternatively, in case that a screw protrusion is formed at a side of the first pipe body 110 facing the refrigerant flowing space 111, the screw protrusion abuts against an outer wall of the main pipe 200 to form a screw flow passage.

A part of the screw-shaped coolant flow channel 201 is formed between two adjacent screw-shaped protrusions. In the case where the screw protrusions are continuously distributed and all abut against the outer wall of the main pipe 200, the screw-shaped flow passages of the respective sections are connected to each other to form screw flow passages. The refrigerant flowing in the heat exchange space 202 can flow only along the screw flow path. With such arrangement, the flow path of the refrigerant in the heat exchange space 202 can be prolonged, so that the refrigerant in the heat exchange space 202 can exchange heat with the refrigerant in the main pipeline 200 and the refrigerant in the throttle channel 130 more fully.

Optionally, the first tube body 110 is provided with a first interface, and the first end of the throttling flow channel 130 is communicated with the heat exchange space 202 through the first interface.

In this case, the throttle flow path 130 serves only as a throttle member of the heat exchange device itself. That is, the throttle flow passage 130 and the heat exchanging space 202 cooperate together to reduce the temperature of the refrigerant in the main pipe 200. The throttling flow passage 130 mainly plays a role in throttling, and the heat exchange space 202 plays a role in evaporation. The evaporation and heat absorption of the refrigerant are mainly performed in the heat exchange space 202. With such arrangement, the liquid refrigerant is evaporated in the heat exchange space 202 to absorb heat, thereby reducing the temperature of the refrigerant flowing through the main pipeline 200.

Optionally, the heat exchange device further includes a connecting pipeline 300, one end of the connecting pipeline 300 is communicated with the refrigerant flow channel 201 of the main pipeline 200, the other end is communicated with the second end of the throttling flow channel 130, and a part of liquid refrigerant flowing through the main pipeline 200 enters the throttling flow channel 130 through the connecting pipeline 300.

The main pipeline 200 is supplied with flowing liquid refrigerant, and one part of the liquid refrigerant flowing through the main pipeline 200 serves as a cooled object, and the other part serves as a cooling means. Specifically, a part of the refrigerant continues to flow in the refrigerant flow channel 201 of the main pipe 200 along the flow direction given by the refrigerant circulation system, and another part of the refrigerant enters the throttle flow channel 130. After the liquid refrigerant enters the throttling flow passage 130, the pressure gradually decreases under the throttling action of the throttling flow passage 130. With the pressure of the high-pressure liquid refrigerant being reduced, the liquid refrigerant evaporates into a gaseous state and absorbs heat in the phase change process. The refrigerant in the throttling branch pipe evaporates and absorbs heat, and the heat is absorbed from the first part of the refrigerant in the refrigerant flowing space 111 through the pipe wall of the throttling branch pipe and the pipe wall of the heat exchange pipe, so that the temperature of the refrigerant flowing through the refrigerant flowing space 111 is reduced.

With the adoption of the arrangement form, the heat exchange device is provided with only one liquid refrigerant inlet on the whole, so that the heat exchange device is beneficial to being mounted to a refrigerant circulation system. In addition, when the supercooling degree of the liquid refrigerant flowing through the heat exchange tube is large, the liquid refrigerant is not easy to evaporate and absorb heat in the throttling branch pipe; the liquid refrigerant flowing through the heat exchange tube is easy to evaporate and absorb heat in the throttling branch tube when the superheat degree of the liquid refrigerant is smaller. That is, the heat exchange device can realize the self-adaptive adjustment of the supercooling degree of the liquid refrigerant flowing through the heat exchange tube through the structural arrangement.

Optionally, the diameter of the throttling channel is greater than or equal to 1.5 millimeters.

In general, the combination of the length and the inner diameter of the capillary tube is to balance the mass flow rate of the refrigerant in the throttle tube, the throttle resistance and the refrigerant filling amount of the refrigerant circulation system to achieve the highest refrigeration efficiency. For the throttling flow passage, the refrigerant flowing through the throttling main pipe is less, the association relation between the mass flow and the refrigerant filling amount is weaker, and the throttling flow passage can be provided with a longer length and a larger pipe diameter so as to improve the heat exchange effect.

The diameter of the throttling flow passage is larger, and the throttling flow passage needs to be provided with a longer length to obtain the expected throttling effect. This increases the likelihood of choking the flow restriction and increases the cost of the heat exchange device. The diameter of the throttling flow passage is smaller than or equal to 4 mm, the length of the throttling flow passage is shorter, and the cost of the heat exchange device is lower.

Alternatively, the equivalent diameter of the throttle flow passage 130 is less than or equal to 4 millimeters.

The diameter of the throttling flow passage is larger, and the throttling flow passage needs to be provided with a longer length to obtain the expected throttling effect. This increases the likelihood of choking the flow restriction and increases the cost of the heat exchange device. The diameter of the throttling flow passage is smaller than or equal to 4 mm, the length of the throttling flow passage is shorter, and the cost of the heat exchange device is lower.

Alternatively, the pitch of the restriction 130 is greater than or equal to 2 millimeters and less than or equal to 100 millimeters.

If the pitch is smaller, the equivalent diameter of the throttle passage 130 is correspondingly smaller, which results in greater throttle resistance and reduced flow. If the pitch is large, the length of the throttle flow path 130 is short and the heat exchanging effect is poor. The pitch of the spiral part is between 2 mm and 100 mm, so that a proper throttling resistance can be provided, and the heat exchange between the refrigerant in the throttling flow passage 130 and the refrigerant in the heat exchange space 202 is facilitated.

Alternatively, the diameter of the outer tube 100 is greater than or equal to 30 millimeters.

The diameter of the outer tube 100 is greater than or equal to 30 mm, and a large heat exchange space 202 is formed between the outer tube 100 and the inner tube. With such arrangement, the refrigerant in the heat exchange space 202 and the refrigerant in the main pipeline 200 are facilitated to exchange heat.

The cross section of the throttle flow path 130 may be rectangular, elliptical, or the like. The equivalent diameter of the throttle flow path 130 is the diameter of a cylindrical passage of the same length and having the same throttle capability. The equivalent diameter of the throttle runner 130 is large, and the throttle manifold needs to be provided with a long length to obtain a desired throttle effect. This increases the likelihood of blockage of the flow restriction 130 and increases the cost of the heat exchange device. The equivalent diameter of the throttling flow passage 130 is smaller than or equal to 4 mm, the length of the throttling flow passage 130 is shorter, and the cost of the heat exchange device is lower.

Optionally, the outer tube 100 is provided with a first interface and a second interface which are communicated with the heat exchange space 202, the first end of the throttling channel 130 is connected to the first interface, the refrigerant entering the heat exchange space 202 flows out from the second interface, and the first interface and the second interface are respectively positioned at two ends of the threaded channel.

The outer tube 100 is provided with a first port and a second port, and the flow direction of the refrigerant in the heat exchange space 202 is from the first port to the second port. The first interface and the second interface are respectively located at two ends of the threaded flow channel, so that the travel of the refrigerant in the heat exchange space 202 can be increased, and the heat exchange effect of the refrigerant in the heat exchange space 202 and the refrigerant in the main pipeline 200 is improved.

Optionally, the second interface is provided on an upward side of the outer tube 100.

The upward facing side of the outer tube 100 is in terms of the heat exchanger in the use state. Illustratively, in the case of a vertical arrangement of the outer tube 100, the second interface opens at an upward end face of the outer tube 100; in the case that the outer tube 100 is disposed laterally, the second port is opened at a side surface of the outer tube 100, and the second port is opened upward.

The refrigerant entering the heat exchange space 202 is evaporated and sucked and then leaves the heat exchange space 202 from the second interface. The refrigerant in the heat exchange space 202 is in a gaseous state or a state where both gas and liquid phases coexist. The second interface is disposed on an upward side of the outer tube 100, and the refrigerant can complete gas-liquid separation in the heat exchange space 202 under the effect of the density difference of the gas-liquid two-phase refrigerant, so as to avoid the liquid refrigerant flowing out from the second interface.

Optionally, the first interface is formed on a downward surface of the outer tube 100.

Likewise, the downward facing side of the outer tube 100 is referred to as the heat exchanger in the use state. The first interface is formed on the downward side of the outer tube 100, which can improve the ordering of the refrigerant flowing in the heat exchange space 202 and reduce the noise generated when the liquid refrigerant enters the heat exchange space 202 during the operation of the refrigerant circulation system.

Referring to fig. 1-6, an embodiment of the disclosure provides a refrigerant circulation system, where the refrigerant circulation system includes a compressor 20, a condenser 30, a throttling device 40, an evaporator 50, and the heat exchange device 10 described above, where a suction end of the compressor 20 is connected to an air outlet end of the throttling channel 130; the liquid outlet end of the condenser 30 is communicated with a refrigerant inlet of the refrigerant flowing space 111, and the air inlet end is communicated with exhaust gas of the compressor 20; the liquid inlet end of the throttling device 40 is communicated with a refrigerant outlet of the refrigerant flowing space 111; the liquid inlet end of the evaporator 50 is connected to the liquid outlet end of the throttle device 40, and the air outlet end is connected to the air suction end of the compressor 20.

The refrigerant circulation system provided by the embodiment of the disclosure is a refrigerant circulation system with a secondary supercooling function. Illustratively, the refrigerant circulation system cools the high temperature refrigerant discharged through the compressor 20 during the cooling condition in the condenser 30. The high-temperature gaseous refrigerant is condensed into a high-pressure liquid refrigerant in the condenser 30, and flows to the heat exchanger 10. The high pressure liquid refrigerant entering the heat exchange device 10 continues to flow partially along the main line 200 and partially along the throttling branch into the heat exchange space 202. The pressure of the refrigerant entering the heat exchange space 202 is reduced and the refrigerant evaporates into a gaseous state. During the evaporation process of the refrigerant, heat is absorbed from the refrigerant in the main pipeline 200, so that the temperature of the high-pressure liquid refrigerant in the main pipe is reduced, that is, the supercooling degree of the high-pressure liquid refrigerant in the main pipeline 200 is increased. The refrigerant in the heat exchange space 202 flows out of the second port and then returns to the suction end of the compressor 20. The liquid refrigerant in the main pipeline 200 sequentially flows through the throttling device 40, throttles and depressurizes, then enters the evaporator 50, absorbs heat in evaporation and returns to the suction end of the compressor 20.

By using the refrigerant circulation system provided by the embodiment of the disclosure, the heat exchange device 10 adopts a mode that the outer pipe 100 is sleeved with the main pipeline 200, so that the volume is small, the cost is low, and the installation position is flexible; a part of the refrigerant exchanges heat with the refrigerant in the main pipeline 200 through the heat exchange space 202, and the refrigerant in the main pipeline 200 can have larger supercooling degree, so that the refrigerating and heating effects of the refrigerant circulation system can be improved; a throttling flow passage 130 is formed between the inner wall and the outer wall of the outer tube 100, the appearance of the heat exchange device 10 is neat, and the throttling effect is stable; the refrigerant in the throttling channel 130 indirectly exchanges heat with the liquid refrigerant in the main pipeline 200, and the liquid refrigerant in the main pipeline 200 can obtain larger supercooling degree.

Alternatively, the suction end of the compressor 20 includes a suction port 21 and a jet port 22, the suction port 21 communicates with the outlet end of the evaporator 50, and the jet port 22 communicates with the second port of the outer tube 100.

The compressor 20 is a rotor compressor 20, and a piston cylinder of the rotor compressor 20 is provided with an air inlet and an injection port 22. When the suction pressure of the compressor 20 is high, the compressor 20 sucks the gaseous refrigerant from the heat exchange space 202 of the heat exchange device 10, thereby increasing the refrigerant mass flow rate in the refrigerant circulation system. By this form of the enhanced vapor injection, the heating effect of the compressor 20, particularly in a low temperature environment, can be improved.

The above description and the drawings illustrate embodiments of the disclosure sufficiently to enable those skilled in the art to practice them. Other embodiments may include structural and other modifications. The embodiments represent only possible variations. Individual components and functions are optional unless explicitly required, and the sequence of operations may vary. Portions and features of some embodiments may be included in, or substituted for, those of others. The embodiments of the present disclosure are not limited to the structures that have been described above and shown in the drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims (10)

1. A heat exchange device for a refrigerant circulation system, comprising:

a first pipe body defining a refrigerant flow space therein;

the second pipe body is sleeved on the first pipe body, a throttling flow passage is formed between the first pipe body and the second pipe body, and the refrigerant flowing through the throttling flow passage exchanges heat with the refrigerant flowing through the refrigerant flowing space.

2. A heat exchange device according to claim 1, wherein,

the throttling flow passage is spiral, and is wound around the refrigerant flowing space.

3. The heat exchange device of claim 2, further comprising:

the spiral piece, inwards one side butt in the outer wall of first body, outwards one side butt in the inner wall of second body, the spiral piece is in first body with the second body between inject the heliciform throttling flow way.

4. A heat exchange device according to claim 2, wherein,

the first pipe body is provided with a threaded groove towards the second pipe body, and an opening of the threaded groove is abutted against the inner wall of the second pipe body to form the spiral throttling flow passage; and/or the number of the groups of groups,

the second pipe body is provided with a threaded groove towards the first pipe body, and an opening of the threaded groove is abutted against the outer wall of the first pipe body to form a spiral throttling flow passage.

5. A heat exchange device according to claim 4 wherein,

and under the condition that the first pipe body is provided with a threaded groove towards the second pipe body, a threaded protrusion is formed on one surface of the first pipe body, which faces the refrigerant flowing space, corresponding to the threaded groove.

6. The heat exchange device of any one of claims 1 to 5, further comprising:

the main pipeline is internally provided with a refrigerant flow passage, a heat exchange space is defined between the first pipe body and the outer wall of the main pipeline, the refrigerant flow space comprises the heat exchange space and the refrigerant flow passage, the refrigerant flowing through the throttling flow passage exchanges heat with the refrigerant flowing through the heat exchange space, and the refrigerant flowing through the heat exchange space exchanges heat with the refrigerant flowing through the refrigerant flow passage.

7. A heat exchange device according to claim 6 wherein,

and under the condition that a threaded protrusion is formed on one surface of the first pipe body facing the refrigerant flowing space, the threaded protrusion is abutted against the outer wall of the main pipeline to form a threaded flow passage.

8. A heat exchange device according to claim 6 wherein,

the first pipe body is provided with a first interface, and the first end of the throttling flow passage is communicated with the heat exchange space through the first interface.

9. The heat exchange device of claim 6, further comprising:

and one end of the connecting pipeline is communicated with the refrigerant flow passage of the main pipeline, the other end of the connecting pipeline is communicated with the second end of the throttling flow passage, and a part of liquid refrigerant flowing through the main pipeline enters the throttling flow passage through the connecting pipeline.

10. A refrigerant circulation system, comprising:

a heat exchange device as claimed in any one of claims 1 to 9; and, a step of, in the first embodiment,

the air suction end of the compressor is communicated with the air outlet end of the throttling flow passage;

the liquid outlet end of the condenser is communicated with a refrigerant inlet of the refrigerant flowing space, and the air inlet end of the condenser is communicated with exhaust gas of the compressor;

a throttling device, wherein a liquid inlet end is communicated with a refrigerant outlet of the refrigerant flowing space;

and the liquid inlet end of the evaporator is communicated with the liquid outlet end of the throttling device, and the air outlet end of the evaporator is communicated with the air suction end of the compressor.