CN221173073U - Plate heat exchanger and refrigerant circulation system - Google Patents

Abstract

The application relates to the technical field of air conditioning, and discloses a plate heat exchanger, which comprises a first plate body and a second plate body, wherein a first refrigerant flow passage is defined in the first plate body; the second plate body is attached to the first plate body, and a second refrigerant flow passage is defined in the second plate body; the first plate body and/or the second plate body are/is internally provided with a throttling flow passage, the outlet end of the throttling flow passage is communicated with the first end of the second refrigerant flow passage, and the refrigerant entering the second refrigerant flow passage through the throttling flow passage absorbs heat from the first plate body so as to reduce the temperature of the refrigerant in the first refrigerant flow passage. The application also discloses a refrigerant circulation system.

Description

Plate heat exchanger and refrigerant circulation system

Technical Field

The application relates to the technical field of air conditioning, in particular to a plate heat exchanger and a refrigerant circulating 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, and the air conditioner 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 a compressor. The air conditioner performs secondary supercooling on the refrigerant through the plate heat exchanger and the auxiliary electronic expansion valve, so that the supercooling degree of the liquid refrigerant is 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:

The secondary supercooling mode of the plate heat exchanger combined with the auxiliary electronic expansion valve is complex in structure and high in cost.

It should be noted that the information disclosed in the above background section is only for enhancing understanding of the background of the 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 utility model

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 plate heat exchanger and a refrigerant circulation system, so as to simplify a secondary supercooling structure and reduce the cost of the refrigerant circulation system.

In some embodiments, the plate heat exchanger includes a first plate body and a second plate body, wherein the first plate body defines a first refrigerant flow passage therein; the second plate body is attached to the first plate body, and a second refrigerant flow passage is defined in the second plate body; the first plate body and/or the second plate body are/is internally provided with a throttling flow passage, the outlet end of the throttling flow passage is communicated with the first end of the second refrigerant flow passage, and the refrigerant entering the second refrigerant flow passage through the throttling flow passage absorbs heat from the first plate body so as to reduce the temperature of the refrigerant in the first refrigerant flow passage.

In some embodiments, the first plate and/or the second plate are provided with an orifice, and the orifice defines the orifice flow channel.

In some embodiments, the first cooling medium channel comprises a plurality of first plate bodies, wherein the first cooling medium channels of the plurality of first plate bodies are communicated to form a first cooling medium channel.

In some embodiments, the second cooling medium channel comprises a plurality of second plates, wherein the second cooling medium channels of the plurality of second plates are communicated to form a second cooling medium channel, and the plurality of first plates and the plurality of second plates are alternately arranged.

In some embodiments, the orifice is formed in one of the plurality of first plates, and the thickness of the first plate with the orifice is greater than the thickness of the first plate without the orifice.

In some embodiments, the orifice is formed in one of the plurality of second plates, and the thickness of the second plate with the orifice is greater than the thickness of the second plate without the orifice.

In some embodiments, the first plate body is provided with a first via hole, a second via hole, a first through hole and a second through hole, the inner wall of the first through hole is provided with a first liquid inlet, the inner wall of the second through hole is provided with a first liquid outlet, and a first refrigerant flow channel is defined between the first liquid inlet and the first liquid outlet; the second plate body is provided with a third through hole and a fourth through hole, the inner wall of the third through hole is provided with a second liquid inlet, the inner wall of the fourth through hole is provided with a second liquid outlet, and a second refrigerant flow channel is defined between the second liquid inlet and the second liquid outlet; the first through hole of the first plate corresponds to the third through hole of the second plate, and the second through hole of the first plate corresponds to the fourth through hole of the second plate.

In some embodiments, the second plate body is provided with a third via hole and a fourth via hole, the first through hole of the first plate body corresponds to the third via hole of the second plate body, and the second through hole of the first plate body corresponds to the fourth via hole of the second plate body.

In some embodiments, the plate heat exchanger further comprises a three-way connecting piece, wherein the three-way connecting piece is provided with a liquid inlet, a first liquid outlet and a second liquid outlet, the first liquid outlet is communicated with the liquid inlet end of the first refrigerant flow channel, and the second liquid outlet is communicated with the first end of the throttling flow channel.

In some embodiments, the first plate body is provided with a first positioning hole, and the second plate body is provided with a second positioning hole corresponding to the first positioning hole; the plate heat exchanger further comprises a locating pin, and the locating pin penetrates through the first locating hole and the second locating hole.

In some embodiments, the refrigerant circulation system includes the above-mentioned plate heat exchanger, a compressor, a condenser, a throttling device, and an evaporator, wherein a suction end of the compressor is communicated with a discharge end of the second refrigerant flow channel; the liquid outlet end of the condenser is communicated with the liquid inlet end of the first refrigerant flow channel and the liquid inlet end of the throttling flow channel, and the air inlet end is communicated with the exhaust of the compressor; the liquid inlet end of the throttling device is communicated with the liquid outlet end of the first refrigerant flow passage; 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 plate heat exchanger and the refrigerant circulation system provided by the embodiment of the disclosure can realize the following technical effects:

The plate heat exchanger is provided with a throttling flow passage, and the plate heat exchanger plays a role in heat exchange and simultaneously plays a role in throttling, so that the structure of the supercooling device is simplified and the cost of the supercooling device is reduced; the throttling and depressurization of the liquid refrigerant is realized through the throttling flow passage, so that the cost is low, and the depressurization effect is reliable; the refrigerant flowing through the second refrigerant flow channel absorbs heat through evaporation, and the refrigerant flowing through the first refrigerant flow channel can obtain larger supercooling degree, so that the refrigerating and heating effects of the refrigerant circulation system can be improved.

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 view of a plate heat exchanger according to an embodiment of the present disclosure;

FIG. 2 is a schematic view of another plate heat exchanger provided in an embodiment of the present disclosure;

FIG. 3 is a schematic view of another plate heat exchanger provided in an embodiment of the present disclosure;

FIG. 4 is a schematic view of another plate heat exchanger provided in an embodiment of the present disclosure;

fig. 5 is a schematic structural view of a first plate body of a plate heat exchanger according to an embodiment of the present disclosure;

Fig. 6 is a schematic structural view of a second plate body of a plate heat exchanger according to an embodiment of the present disclosure;

fig. 7 is a schematic diagram of a refrigerant circulation system according to an embodiment of the disclosure.

Reference numerals:

100: a first plate body; 101: a first via; 102: a second via; 103: a first through hole; 104: a second through hole; 105: a first refrigerant flow passage; 106: a first positioning hole; 200: a second plate body; 201: a third via; 202: a fourth via; 203: a third through hole; 204: a fourth through hole; 205: a second refrigerant flow path; 206: a second positioning hole; 210: an orifice; 300: a positioning pin; 400: a three-way connection; 10: a heat exchange device; 20: a compressor; 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, and the air conditioner 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 a compressor. The air conditioner performs secondary supercooling on the refrigerant through the plate heat exchanger and the auxiliary electronic expansion valve, so that the supercooling degree of the liquid refrigerant is improved. The related art has the problems that the plate heat exchanger combined with the auxiliary electronic expansion valve has a complex secondary supercooling form structure and high cost.

In order to simplify the structure of the secondary supercooling and thereby reduce the cost of the refrigerant circulation system, referring to fig. 1 to 6, an embodiment of the present disclosure provides a plate heat exchanger, which includes a first plate body 100 and a second plate body 200, wherein a first refrigerant flow channel 105 is defined inside the first plate body 100; the second plate 200 is attached to the first plate 100, and a second refrigerant channel 205 is defined in the second plate 200; the first plate 100 and/or the second plate 200 define a throttling channel therein, an outlet end of the throttling channel is communicated with a first end of the second refrigerant channel 205, and the refrigerant entering the second refrigerant channel 205 through the throttling channel absorbs heat from the first plate 100 to reduce the temperature of the refrigerant in the first refrigerant channel 105.

The plate heat exchanger comprises a plurality of heat exchange plates, and the thickness dimension of the heat exchange plates is far smaller than the length-width dimension of the heat exchange plates. The plurality of heat exchange plates are stacked along the thickness direction, and the medium in the adjacent heat exchange plates exchanges heat through the plate bodies of the heat exchange plates.

Specifically, the plate heat exchanger provided in the embodiment of the present disclosure includes at least a first plate body 100 and a second plate body 200. The first plate 100 defines a first refrigerant flow passage 105 therein, and the second plate 200 defines a second refrigerant flow passage 205 therein. The refrigerant flowing through the first refrigerant flow channel 105 exchanges heat with the refrigerant flowing through the second refrigerant flow channel 205 through the wall surfaces adjacent to the first plate 100 and the second plate 200.

The plate heat exchanger is also constructed with a throttling flow passage in communication with the second refrigerant flow passage 205.

In the working state of the plate heat exchanger, a part of liquid refrigerant enters the first refrigerant flow channel 105, and the other part of liquid refrigerant enters the second refrigerant flow channel 205 through the throttling flow channel. The refrigerant entering the second refrigerant flow path 205 evaporates into a gaseous state due to the pressure decrease and absorbs heat during the evaporation process. The refrigerant in the second refrigerant flow channel 205 evaporates to absorb heat from the liquid refrigerant in the first refrigerant flow channel 105, thereby reducing the temperature of the refrigerant in the first refrigerant flow channel 105, i.e., obtaining a greater supercooling degree of the refrigerant flowing through the first refrigerant flow channel 105.

As an implementation of the plate heat exchanger configured with a throttling flow channel, the first plate body 100 is configured with a throttling flow channel as described above.

As another implementation of the plate heat exchanger configured with a throttling flow channel, the second plate body 200 is configured with a throttling flow channel as described above.

As another implementation of the plate heat exchanger configured with a flow restriction, a part of the flow restriction is located in the first plate body 100 and another part is located in the second plate body 200. The first plate body 100 and the second plate body 200 together construct a throttle flow passage.

The length and equivalent diameter of the throttle flow passage can be measured through experiments, and can also be determined according to the following formula:

Wherein L is the length of the throttling flow passage, d is the equivalent diameter of the throttling flow passage, deltaP is the pressure change value before and after throttling, q is the refrigerant mass flow, and mu is the refrigerant viscosity.

By using the plate heat exchanger provided by the embodiment of the disclosure, the plate heat exchanger is provided with the throttling flow channel, and the plate heat exchanger plays a role in heat exchange and simultaneously plays a role in throttling, so that the structure of the supercooling device is simplified and the cost of the supercooling device is reduced; the throttling and depressurization of the liquid refrigerant is realized through the throttling flow passage, so that the cost is low, and the depressurization effect is reliable; the refrigerant flowing through the second refrigerant flow channel 205 absorbs heat by evaporation, and the refrigerant flowing through the first refrigerant flow channel 105 can obtain a larger supercooling degree, so that the refrigerating and heating effects of the refrigerant circulation system can be improved.

Optionally, the first plate 100 and/or the second plate 200 are provided with an orifice 210, and the orifice 210 defines a throttle flow channel.

As one implementation, the first plate 100 is provided with an orifice 210. The orifice 210 is opened in a direction penetrating the first plate body 100 so as to define a throttle flow passage in the first plate body 100. The second plate 200 is attached to the first plate 100, and a liquid inlet end of the second refrigerant channel 205 of the second plate 200 is in butt joint with an orifice 210 formed in the first plate 100.

As another implementation form, the second plate 200 is provided with an orifice 210, and an extending direction of the orifice 210 is at least partially along a thickness direction of the second plate 200. The end of the orifice 210 is abutted against the liquid inlet end of the second refrigerant flow passage 205 formed in the second plate 200. In this implementation, the inlet of the second refrigerant flow channel 205 is preferably formed in the inner wall of the orifice 210. This facilitates the interface of the orifice 210 with the second refrigerant flow passage 205.

As another implementation, the orifice 210 includes a first hole section and a second hole section, where the first hole section is formed in the first plate 100, and the second hole Duan Kai is formed in the second plate 200. The first hole section is butted with the second hole section after the first plate body 100 and the second plate body 200 are stacked. In this implementation, the orifice 210 may have a longer length in the case of the first plate body 100 and the second plate body 200 having a limited thickness. The greater the length of the orifice 210, the greater the diameter when achieving the same restriction. Larger diameters of the orifice 210 may mitigate the likelihood of the orifice 210 becoming plugged.

Optionally, the first plate 100 includes a plurality of first plate bodies 100, and the first refrigerant channels 105 of the plurality of first plate bodies 100 are communicated to form a first refrigerant channel.

The plate heat exchanger includes a plurality of first plate bodies 100, and the refrigerant flowing through the first refrigerant passage has a larger heat exchange area. By adopting the arrangement mode, the supercooling effect on the liquid refrigerant can be improved.

Alternatively, the plate heat exchanger comprises two first plate bodies 100 and one second plate body 200, the second plate body 200 being located between two layers of the first plate bodies 100.

The two first plate bodies 100 are located on the outward facing sides of the plate heat exchanger, and the two sides of the second plate body 200 are covered by the two first plate bodies 100. The temperature of the refrigerant entering the first plate 100 is relatively high, typically above the ambient temperature. With this arrangement, heat can be exchanged with the environment through the two outwardly facing surfaces of the two first plates 100. Thereby reducing the temperature of the refrigerant flowing through the first refrigerant passage. The temperature of the refrigerant entering the second plate 200 after evaporation is lower, typically lower than the ambient temperature. The second plate 200 is located between the two layers of the first plate 100, so that the heat absorption of the refrigerant in the second plate 200 from the environment can be reduced or avoided, and the refrigerant flowing through the first refrigerant channel 105 is beneficial to absorb heat from the refrigerant in the first refrigerant channel, so that the temperature of the refrigerant flowing through the first refrigerant channel is reduced.

Optionally, the first refrigerant channels 105 of the plurality of first plates 100 are connected in parallel.

By adopting the arrangement form, the design and the assembly of the plate heat exchanger are facilitated on one hand; on the other hand, the flow resistance of the refrigerant flowing through the first refrigerant passage can be reduced, so that the flow rate of the refrigerant flowing through the plate heat exchanger is improved, and the heat exchange efficiency of the plate heat exchanger is improved.

Optionally, the second cooling medium channel 205 of the second plates 200 is connected to form a second cooling medium channel, where the first plates 100 and the second plates 200 are alternately arranged.

Illustratively, the plate heat exchanger comprises three layers of first plate bodies 100 and two layers of second plate bodies 200, each second plate body 200 being located between two adjacent layers of first plate bodies 100. Thus, the heat exchange areas of the first refrigerant passage and the second refrigerant passage are four plate surfaces of the second plate 200. The plate heat exchanger includes a plurality of second plate bodies 200, which can increase the heat exchange area between the refrigerant flowing through the second refrigerant flow channel 205 and the refrigerant flowing through the first refrigerant flow channel 105.

Optionally, the second refrigerant channels 205 of the plurality of second plates 200 are connected in parallel.

By adopting the arrangement form, the design and the assembly of the plate heat exchanger are facilitated on one hand; on the other hand, the flow resistance of the refrigerant flowing through the second refrigerant passage can be reduced, so that the flow rate of the refrigerant flowing through the plate heat exchanger is improved, and the heat exchange efficiency of the plate heat exchanger is improved.

Alternatively, the orifice 210 is formed in one first plate 100 of the plurality of first plates 100, and the thickness of the first plate 100 with the orifice 210 is greater than the thickness of the first plate 100 without the orifice 210.

When the orifice 210 is opened to the first plate 100, the length of the orifice 210 is limited to a certain extent by the thickness of the first plate 100. In the case where the length of the orifice 210 is smaller, the equivalent diameter of the orifice 210 is smaller, which increases the risk of clogging the orifice 210. In view of this, when the orifice 210 is opened to the first plate body 100 and the plate heat exchanger includes a plurality of first plate bodies 100, one of the first plate bodies 100 is used as the orifice 210 plate, and the thickness of the orifice 210 plate is larger than the thickness of the other first plate bodies 100.

With such an arrangement, the remaining first plate body 100 may be provided in the same shape or with standard components, other than the orifice 210 plate, facilitating assembly of the plate heat exchanger. In addition, the orifice 210 plate has a large thickness, and the orifice 210 has a large diameter and is not easily blocked.

As a preferred embodiment, the orifice 210 is formed in one of the plurality of first plates 100 that faces outward.

In case the plate heat exchanger comprises a plurality of first plate bodies 100, the outwardly directed first plate bodies 100 are first plate bodies 100 close to the side of the plate heat exchanger where the pipe connection is provided. The orifice 210 is formed in the first plate 100, and the liquid refrigerant evaporates before entering the second refrigerant passage, so as to reduce the temperature of the refrigerant flowing through the first refrigerant passage.

Alternatively, the orifice 210 is formed in one of the plurality of second plates 200, and the thickness of the second plate 200 with the orifice 210 is greater than the thickness of the second plate 200 without the orifice 210.

When the orifice 210 is opened in the second plate 200, the length of the orifice 210 is limited to a certain extent by the thickness of the second plate 200. In the case where the length of the orifice 210 is smaller, the equivalent diameter of the orifice 210 is smaller, which increases the risk of clogging the orifice 210. In view of this, when the orifice 210 is opened to the second plate body 200 and the plate heat exchanger includes a plurality of second plate bodies 200, one of the second plate bodies 200 is used as the orifice 210 plate, and the thickness of the orifice 210 plate is larger than that of the other second plate bodies 200.

With such an arrangement, the remaining second plate body 200 may be provided in the same shape or with standard components, except for the orifice 210 plate, facilitating assembly of the plate heat exchanger. In addition, the orifice 210 plate has a large thickness, and the orifice 210 has a large diameter and is not easily blocked.

As a preferred embodiment, the orifice 210 is formed in one of the plurality of second plates 200 that is outward of the first plate 100.

In case the plate heat exchanger comprises a plurality of second plate bodies 200, the outward second plate body 200 is the second plate body 200 close to the side of the plate heat exchanger where the pipe connection is arranged. The orifice 210 is formed in the second plate 200, and the liquid refrigerant evaporates when entering the second refrigerant passage, so as to reduce the temperature of the refrigerant flowing through the first refrigerant passage.

Optionally, the first plate body 100 is provided with a first via hole 101, a second via hole 102, a first through hole 103 and a second through hole 104, the inner wall of the first through hole 103 is provided with a first liquid inlet, the inner wall of the second through hole 104 is provided with a first liquid outlet, and the first plate body 100 defines a first refrigerant flow channel 105 between the first liquid inlet and the first liquid outlet; the second plate 200 is provided with a third through hole 203 and a fourth through hole 204, the inner wall of the third through hole 203 is provided with a second liquid inlet, the inner wall of the fourth through hole 204 is provided with a second liquid outlet, and a second refrigerant flow channel 205 is defined between the second liquid inlet and the second liquid outlet by the second plate 200; the first via 101 of the first board 100 corresponds to the third through hole 203 of the second board 200, and the second via 102 of the first board 100 corresponds to the fourth through hole 204 of the second board 200.

The first through hole 101 and the second through hole 102 are not communicated with the first refrigerant flow channel 105, and the first through hole 103 and the second through hole 104 serve as a liquid inlet end and a liquid outlet end of the first refrigerant flow channel 105 respectively. The first and second through holes 101 and 102 are used to enable connection lines of the plate heat exchanger to pass through the first plate body 100 and connect to the second refrigerant flow channel 205 of the second plate body 200.

Specifically, the first via 101 penetrates the first board 100 and is abutted against the third through hole 203 of the second board 200, and the second via 102 penetrates the first board 100 and is abutted against the fourth through hole 204 of the second board 200. By adopting the arrangement form, the connecting pipeline of the plate heat exchanger is positioned on one side surface or two side surfaces, which is beneficial to arranging the connecting pipeline for the plate heat exchanger.

As a preferred embodiment, the first via 101 is in seamless connection with the third through hole 203 of the second board 200, and the second via 102 is in seamless connection with the fourth through hole 204 of the second board 200.

In this case, the first and second through holes 101 and 102 of the connection pipe connected to the first plate body 100 can be regarded as the third and fourth through holes 203 and 204 connected to the second plate body 200, thereby achieving connection to the second refrigerant flow passage 205.

With such an arrangement, it is advantageous to provide the plate heat exchanger with connecting lines.

Optionally, the second board 200 is provided with a third via 201 and a fourth via 202, the first through hole 103 of the first board 100 corresponds to the third via 201 of the second board 200, and the second through hole 104 of the first board 100 corresponds to the fourth via 202 of the second board 200.

In the case of a plate heat exchanger comprising a plurality of first plate bodies 100, the second plate body 200 is provided with third and fourth vias 201, 202, which facilitates the simultaneous configuration of connecting tubes for the plurality of first plate bodies 100 of the plate heat exchanger.

Illustratively, the plate heat exchanger comprises two first plate bodies 100 and one second plate body 200, the second plate body 200 being located between the two first plate bodies 100. The two first through holes 103 of the two first plate bodies 100 are connected by the third through hole 201. That is, the first through holes 103 of the two first plates 100 and the third through holes 201 of the second plates 200 together form a liquid inlet channel, and the liquid inlet ends of the first refrigerant channels 105 of the two first plates 100 are connected in parallel to the liquid inlet channel. Correspondingly, the two second through holes 104 of the two first plate bodies 100 are connected through the fourth through hole 202 of the second plate body 200, the second through holes 104 of the two first plate bodies 100 and the fourth through hole 202 of the second plate body 200 together form a liquid outlet flow channel, and the liquid outlet ends of the first refrigerant flow channels 105 of the two first plate bodies 100 are connected in parallel to the liquid outlet flow channel.

By adopting the arrangement form, the mechanism of the plate heat exchanger is simplified, and the connection pipeline is beneficial to the configuration of the plate heat exchanger.

Optionally, the plate heat exchanger further includes a three-way connecting piece 400, the three-way connecting piece 400 is provided with a liquid inlet, a first liquid outlet and a second liquid outlet, the first liquid outlet is communicated with the liquid inlet end of the first refrigerant flow channel 105, and the second liquid outlet is communicated with the first end of the throttling flow channel.

The three-way connecting piece 400 is provided with a liquid refrigerant inlet, the refrigerant entering the three-way connecting piece 400 is divided into two parts, one part enters the first refrigerant flow channel 105 through the first liquid outlet, and the other part enters the second refrigerant flow channel 205 through the throttling flow channel through the second liquid outlet. The refrigerant entering the second refrigerant flow channel 205 absorbs heat by evaporation, thereby reducing the temperature of the refrigerant flowing through the first refrigerant flow channel 105.

By adopting the arrangement form, the plate heat exchanger is provided with only one refrigerant inlet, which is beneficial to assembling the plate heat exchanger to a refrigerant circulation system.

Optionally, the plate heat exchanger further includes a liquid separation plate, the liquid separation plate defines a liquid separation channel therein, the liquid separation plate is further provided with a refrigerant inlet, a first refrigerant outlet and a second refrigerant outlet, the refrigerant inlet is communicated with the liquid separation channel, the first refrigerant outlet is communicated with a liquid inlet end of the first refrigerant channel 105, and the second refrigerant outlet is communicated with a first end of the throttling channel.

A liquid separation plate is arranged to facilitate the distribution of the liquid refrigerant between the first refrigerant flow passage 105 and the second refrigerant flow passage 205; the liquid separation plate can be inserted between the plurality of heat exchange plates of the plate heat exchanger, and the liquid separation plate is arranged to facilitate the arrangement of the plurality of heat exchange plates of the plate heat exchanger and reduce the auxiliary connecting pipelines required by the plate heat exchanger; the liquid separation channel in the liquid separation plate can also accumulate a part of refrigerant, namely the refrigerant can exchange heat with the rest heat exchange plates of the plate heat exchanger through the liquid separation plate, so that the temperature of the refrigerant in the plate heat exchanger is further reduced.

Optionally, the first plate body 100 is provided with a first positioning hole 106, and the second plate body 200 is provided with a second positioning hole 206 corresponding to the first positioning hole 106; the plate heat exchanger further comprises a positioning pin 300, the positioning pin 300 penetrating the first positioning hole 106 and the second positioning hole 206.

The first plate body 100 and the second plate body 200 are coupled together by the positioning pins 300 according to a predetermined relative position. Specifically, the first plate 100 is provided with a first positioning hole 106, the second plate 200 is provided with a second positioning hole 206, and the positioning pin 300 passes through the first positioning hole 106 and the second positioning hole 206 to enable the first plate 100 and the second plate 200 to be in a preset relative position. At the predetermined relative position, the first through hole 103 of the first board 100 is abutted against the third through hole 201 of the second board 200, the second through hole 104 of the first board 100 is abutted against the fourth through hole 202 of the second board 200, the first through hole 101 of the first board 100 is abutted against the third through hole 203 of the second board 200, and the second through hole 102 of the first board 100 is abutted against the fourth through hole 204 of the second board 200.

With such arrangement, positioning and fixing of the first and second plate bodies 100 and 200 are facilitated.

Optionally, the plate heat exchanger includes a plurality of positioning pins 300, the first plate body 100 is provided with a plurality of first positioning holes 106 corresponding to the plurality of positioning pins 300, and the second plate body 200 is provided with a plurality of second positioning holes 206 corresponding to the plurality of first positioning holes 106.

With such arrangement, the installation positioning accuracy and the fixing effect between the first plate body 100 and the second plate body 200 can be further improved.

Referring to fig. 1-7, an embodiment of the disclosure provides a refrigerant circulation system, where the refrigerant circulation system includes the above-mentioned plate heat exchanger 10, the compressor 20, the condenser 30, the throttling device 40, and the evaporator 50, and an air suction end of the compressor 20 is communicated with an air outlet end of the second refrigerant flow channel 205; the liquid outlet end of the condenser 30 is communicated with the liquid inlet end of the first refrigerant flow channel 105 and the liquid inlet end of the throttling flow channel, and the air inlet end is communicated with the exhaust of the compressor 20; the liquid inlet end of the throttling device 40 is communicated with the liquid outlet end of the first refrigerant flow passage 105; 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 plate heat exchanger 10. The high-pressure liquid refrigerant entering the plate heat exchanger 10 continues to flow partially along the first refrigerant flow path 105 and partially through the throttling flow path into the second refrigerant flow path 205. The pressure of the refrigerant entering the second refrigerant flow channel 205 is reduced and the refrigerant evaporates into a gaseous state. During the evaporation process of the refrigerant, heat is absorbed from the first refrigerant flow channel 105, so that the temperature of the high-pressure liquid refrigerant in the first refrigerant flow channel 105 is reduced, that is, the supercooling degree of the refrigerant in the first refrigerant flow channel 105 is increased. The gaseous refrigerant of the second refrigerant flow path 205 returns to the suction end of the compressor 20. The liquid refrigerant flowing out of the first refrigerant flow passage 105 flows through the throttle device 40 in sequence, is throttled and depressurized, enters the evaporator 50, absorbs heat during 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 plate heat exchanger 10 is provided with the throttling flow channel, and the plate heat exchanger 10 plays a role in heat exchange and simultaneously plays a role in throttling, so that the structure of the supercooling device is simplified and the cost of the supercooling device is reduced; the throttling and depressurization of the liquid refrigerant is realized through the throttling flow passage, so that the cost is low, and the depressurization effect is reliable; the refrigerant flowing through the second refrigerant flow channel 205 absorbs heat by evaporation, and the refrigerant flowing through the first refrigerant flow channel 105 can obtain a larger supercooling degree, so that the refrigerating and heating effects of the refrigerant circulation system 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 plate heat exchanger, comprising:

a first plate defining a first refrigerant flow passage therein;

The second plate body is attached to the first plate body, and a second refrigerant flow passage is defined in the second plate body;

The first plate body and/or the second plate body are/is internally provided with a throttling flow passage, the outlet end of the throttling flow passage is communicated with the first end of the second refrigerant flow passage, and the refrigerant entering the second refrigerant flow passage through the throttling flow passage absorbs heat from the first plate body to reduce the temperature of the refrigerant in the first refrigerant flow passage.

2. A plate heat exchanger according to claim 1, wherein,

The first plate body and/or the second plate body is/are provided with throttling holes, and the throttling channels are defined by the throttling holes.

3. A plate heat exchanger according to claim 2, wherein,

The first refrigerant flow channels of the plurality of first plate bodies are communicated to form a first refrigerant passage.

4. A plate heat exchanger according to claim 3, wherein,

The first cooling medium channel is communicated with the second cooling medium channel to form a second cooling medium channel, wherein the first cooling medium channel and the second cooling medium channel are alternately arranged.

5. The plate heat exchanger according to claim 4, wherein,

The first plate body is provided with an orifice, and the thickness of the first plate body provided with the orifice is larger than that of the first plate body not provided with the orifice; or alternatively, the first and second heat exchangers may be,

The throttling hole is formed in one of the second plate bodies, and the thickness of the second plate body with the throttling hole is larger than that of the second plate body without the throttling hole.

6. The plate heat exchanger according to claim 4, wherein,

The first plate body is provided with a first via hole, a second via hole, a first through hole and a second through hole, the inner wall of the first through hole is provided with a first liquid inlet, the inner wall of the second through hole is provided with a first liquid outlet, and a first refrigerant flow channel is defined between the first liquid inlet and the first liquid outlet;

The second plate body is provided with a third through hole and a fourth through hole, the inner wall of the third through hole is provided with a second liquid inlet, the inner wall of the fourth through hole is provided with a second liquid outlet, and a second refrigerant flow channel is defined between the second liquid inlet and the second liquid outlet;

The first through hole of the first plate corresponds to the third through hole of the second plate, and the second through hole of the first plate corresponds to the fourth through hole of the second plate.

7. The plate heat exchanger according to claim 6, wherein,

The second plate body is provided with a third through hole and a fourth through hole, the first through hole of the first plate body corresponds to the third through hole of the second plate body, and the second through hole of the first plate body corresponds to the fourth through hole of the second plate body.

8. A plate heat exchanger according to any one of claims 1 to 7, further comprising:

The three-way connecting piece is provided with a liquid inlet, a first liquid outlet and a second liquid outlet, wherein the first liquid outlet is communicated with the liquid inlet end of the first refrigerant flow channel, and the second liquid outlet is communicated with the first end of the throttling flow channel.

9. The plate heat exchanger according to claim 8, wherein,

The first plate body is provided with a first positioning hole, and the second plate body is provided with a second positioning hole corresponding to the first positioning hole;

The plate heat exchanger further comprises:

and the locating pin penetrates through the first locating hole and the second locating hole.

10. A refrigerant circulation system, comprising:

a plate heat exchanger according to 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 second refrigerant flow passage;

the liquid outlet end of the condenser is communicated with the liquid inlet end of the first refrigerant flow channel and the liquid inlet end of the throttling flow channel, and the air inlet end is communicated with the exhaust of the compressor;

The liquid inlet end of the throttling device is communicated with the liquid outlet end of the first refrigerant flow passage;

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.