CN116412695A - Parallel flow heat exchanger and heat exchange system - Google Patents

Abstract

A parallel flow heat exchanger and heat exchange system, the parallel flow heat exchanger comprising: a first tube comprising a first tube wall, the first tube having a first cavity, the wall surrounding the first cavity comprising the first tube wall; a second pipe arranged in parallel with the first pipe; the heat exchange tube comprises a micro-channel heat exchange tube which is respectively and directly connected with the first tube and the second tube or indirectly connected with the first tube and the second tube; the first piece, at least part first piece is located first intracavity, first piece includes the second pipe wall, first piece has the second chamber, the wall around the second chamber includes the second pipe wall, the second chamber extends along the length direction of first pipe, the second chamber includes first sub-chamber and second sub-chamber, first sub-chamber and first chamber indirect intercommunication, second sub-chamber and first chamber direct intercommunication, first sub-chamber and second sub-chamber direct intercommunication or indirect intercommunication have lengthened the flow length of heat transfer medium at first piece, the flow length of heat exchanger has been increased, be favorable to adjusting the distribution of heat transfer medium, thereby improve heat exchanger performance.

Description

Parallel flow heat exchanger and heat exchange system

[ field of technology ]

The invention relates to the technical field of heat exchange, in particular to a parallel flow heat exchanger and a heat exchange system.

[ background Art ]

The parallel flow heat exchanger is gradually applied to a refrigerating system such as an automobile air conditioner, a household air conditioner, etc. due to advantages of high heat exchange efficiency, small volume, light weight, etc. Collecting pipes are arranged at two ends of the micro-channel flat pipe and used for distributing and collecting heat exchange media.

In some applications, the refrigerant entering the parallel flow heat exchanger for heat exchange is in a two-phase flow state, the two-phase flow refrigerant is distributed in each micro-channel flat tube and each micro-channel of the flat tube, a state which is unfavorable for heat exchange performance can occur, and a distribution part is required to be designed for regulating the distribution of the two-phase flow refrigerant so as to avoid the influence on the performance of the heat exchanger because the two-phase flow refrigerant directly enters into the space of the collecting pipe for distribution.

[ invention ]

The application provides a parallel flow heat exchanger and have heat transfer system of this parallel flow heat exchanger has increased the flow length of heat exchanger, is favorable to adjusting the distribution of heat transfer medium to improve heat exchanger performance.

In a first aspect, embodiments of the present application provide a parallel flow heat exchanger, including: a first tube comprising a first tube wall, the first tube having a first cavity, the wall surrounding the first cavity comprising the first tube wall; a second pipe arranged in parallel with the first pipe; the heat exchange tube comprises a micro-channel heat exchange tube, the micro-channel heat exchange tube is directly connected or indirectly connected with the first tube, and the micro-channel heat exchange tube is directly connected or indirectly connected with the second tube; the first piece, at least part first piece is located first intracavity, and first piece includes the second pipe wall, and first piece has the second chamber, and the wall that surrounds the second chamber includes the second pipe wall, and the second chamber extends along the length direction of first pipe, and the second chamber includes first subchamber and second subchamber, and first subchamber and first chamber indirect intercommunication, second subchamber and first chamber direct intercommunication, first subchamber and second subchamber direct intercommunication or indirect intercommunication.

In the parallel flow heat exchanger provided by the embodiment of the application, because the first subchamber is not directly communicated with the first chamber, the second subchamber is directly communicated with the first chamber, and the first subchamber and the second subchamber are directly communicated or indirectly communicated, when the heat exchange medium needs to be injected into the parallel flow heat exchanger, the heat exchange medium firstly flows into the first subchamber, then flows into the second subchamber due to pressure difference and finally flows into the first chamber, and the second chamber in the first piece is divided into a plurality of subchambers, so that the flow length of the heat exchange medium in the first piece is prolonged, and the heat exchange medium flows into the first chamber after being uniformly distributed along the length direction of the first piece, thereby being beneficial to the distribution of the heat exchange medium in the heat exchange tube; meanwhile, the flow length of the heat exchange medium in the first piece is prolonged, so that the heat exchange medium can be fully mixed in the flowing process of the second cavity, the temperature of the heat exchange medium along the length direction of the first piece is uniformly distributed, and the heat exchange efficiency of the parallel flow heat exchanger is improved.

With reference to the first aspect, in some embodiments, the first member includes a first orifice and a second orifice, the first orifice communicating with the first subchamber and the second subchamber, the second orifice communicating with the first chamber and the second subchamber, at least a portion of the first orifice and at least a portion of the second orifice extending along a length of the first tube; in a first plane perpendicular to the length direction of the first tube, the projection of the second tube wall comprises at least a part of a spiral line and the projection of the second subchamber comprises a plurality of circular rings. The heat exchange medium flows along the spiral line in the second subchamber by the aid of the structural design, so that the flow length of the heat exchange medium in the first piece is prolonged, the first piece is enabled to be in a cylindrical structure formed by winding, a through hole or a through groove is not required to be additionally formed, and production efficiency is improved.

With reference to the first aspect, in some embodiments, the second tube wall comprises a first sub-wall and a second sub-wall, the first sub-wall and the second sub-wall extending in a length direction of the first tube, the first sub-wall and the second sub-wall having a thickness; the first sub-wall comprises one or more first through holes, the first through holes penetrate through the first sub-wall, and the first through holes are communicated with the first sub-cavity and the second sub-cavity; the second sub-wall comprises a plurality of second through holes, the second through holes penetrate through the second sub-wall, at least part of the second through holes are communicated with the second sub-cavity and the first cavity, and the first through holes are indirectly communicated with the second through holes; in a first plane perpendicular to the length direction of the first tube, the projection of the first sub-wall comprises a first circular arc and the projection of the second sub-wall comprises one or more second circular arcs, the circumference of at least one second circular arc being larger than the circumference of the first circular arc. The structural design ensures that the first piece presents a multi-layer sleeve structure, simplifies the production process of the first piece, and the second subchamber is divided into a plurality of subchambers, thereby lengthening the flow length of the heat exchange medium in the first piece.

With reference to the first aspect, in some embodiments, in the first plane, a projected center of the at least one first via and a projected center of the at least one second via are collinear. The heat exchange medium which flows out from the first through hole and is dispersed into two flows respectively flows through the flow length of the same length and then is collected to the second through hole at the same time, so that the heat exchange medium is further ensured to flow into the first cavity through the second through hole after being uniformly distributed along the length direction of the first piece.

With reference to the first aspect, in some embodiments, in the first plane, the projection of the second sub-wall comprises at least three second arcs, the second arcs comprising one or more radii, at least one radius of one second arc being different from at least one radius of another second arc; in the radial direction of the first pipe, the maximum difference of the radius values between every two adjacent second circular arcs is inversely proportional to the distance between any one of the second circular arcs and the first circular arc. The structural design is more suitable for the state change of the heat exchange medium in the flowing process, and is beneficial to the improvement of the heat exchange performance.

With reference to the first aspect, in some embodiments, the first sub-wall has a smaller number of first through holes than the second sub-wall has second through holes; and/or the sum of the flow areas of the first through holes is smaller than the sum of the flow areas of the second through holes. The structural design ensures that when the heat exchange medium flows into the first cavity from the second through holes, the heat exchange medium can be accelerated to flow out of the second subchamber from the second through holes, so that the accumulation of the heat exchange medium in the first part is avoided, the filling quantity of the heat exchange medium is further reduced, and the distribution difference of the heat exchange medium on a plurality of heat exchange pipes between two adjacent second through holes is reduced.

With reference to the first aspect, in some embodiments, in the first plane, the projection of the second sub-wall includes a second arc, the second arc includes projections of a plurality of second through holes, and the number of second through holes is greater than the number of first through holes. The heat exchange medium flows into the first cavity through the first subchamber, the first through hole, the second subchamber and the second through hole in sequence, so that the heat exchange medium is distributed uniformly along the length direction of the first piece and then redistributed to each heat exchange tube, and the distribution difference of the heat exchange medium on the plurality of heat exchange tubes is reduced.

In combination with the first aspect, in some embodiments, in the first plane, the projection of the second sub-wall comprises two second arcs, wherein, in a radial direction of the first tube, one second arc close to the first arc comprises a projection of a plurality of second through holes, and the number of second through holes is larger than the number of first through holes, and the other second arc far from the first arc comprises a projection of at least one elongated slot. The first piece is of an inner-outer three-layer sleeve structure due to the structural design, and the second arc far away from the first arc comprises the projection of at least one long groove, namely the long groove is formed in the outermost wall of the second sub-wall, so that the resistance of the heat exchange medium in the flowing process is reduced, the influence on the side pressure of the heat exchange medium is reduced, and the heat exchange performance is improved; meanwhile, the long groove has larger flow area, so that the difference of distribution of heat exchange media on the plurality of heat exchange tubes can be reduced.

With reference to the first aspect, in some embodiments, a ratio of the number of first vias to the number of second vias is less than or equal to 1/2. The heat exchange medium flows into the first pipe after being uniformly distributed along the length direction of the first piece by the structural design, and meanwhile, the distribution difference of the heat exchange medium on each heat exchange pipe is reduced.

In a second aspect, embodiments of the present application provide a parallel flow heat exchanger, including: a heat exchange tube having a plurality of channels extending along a length direction thereof; the first component is directly connected or indirectly connected with the heat exchange tube, the first component comprises a first tube wall, the first component is provided with a first cavity, the wall surrounding the first cavity comprises the first tube wall, the first component further comprises a first plate and a second plate, the first plate and the second plate extend along the length direction of the first component, at least part of the first plate and at least part of the second plate are positioned in the first cavity, the first plate and the second plate are arranged along the width direction or the height direction of the first component, the first plate is connected with the inner wall of the first tube wall, the second plate is connected with the inner wall of the first tube wall, the first cavity comprises a first subchamber, a second subchamber and a third subchamber, and the third subchamber is directly communicated with a plurality of channels of the heat exchange tube; the first plate includes a first channel and the second plate includes a second channel, the first channel communicates with the first subchamber and the second subchamber, the second channel communicates with the second subchamber and the third subchamber, and the first channel communicates with the second channel indirectly.

In the parallel flow heat exchanger provided by the embodiment of the application, since the first component comprises the first plate and the second plate which are positioned in the first cavity, the first plate and the second plate can divide the first cavity into the first subchamber, the second subchamber and the third subchamber, when the heat exchange medium needs to be injected into the parallel flow heat exchanger, the heat exchange medium firstly flows into the first subchamber, then flows into the second subchamber from the first channel and flows into the third subchamber from the second channel due to pressure difference and finally flows into a plurality of channels of the heat exchange tube, so that the flow length of the heat exchange medium in the first component is prolonged, and the heat exchange medium flows into the plurality of channels of the heat exchange tube after being uniformly distributed along the length direction of the first component, thereby being beneficial to the distribution of the heat exchange medium in the heat exchange tube; meanwhile, the flow length of the heat exchange medium in the first component is prolonged, so that the heat exchange medium can be fully mixed in the flowing process of the first cavity, the temperature of the heat exchange medium along the length direction of the first component is uniformly distributed, and the heat exchange efficiency of the parallel flow heat exchanger is improved.

With reference to the second aspect, in some embodiments, the sum of the flow areas of the first channels is less than the sum of the flow areas of the second channels. The heat exchange medium in the second subchamber can flow into the third subchamber from the second channel and finally flow into a plurality of channels of the heat exchange tube through the structural design, so that accumulation of the heat exchange medium in the first assembly is avoided, and the filling quantity of the heat exchange medium is reduced.

With reference to the second aspect, in some embodiments, the first channel comprises a through hole or an elongated slot; and/or the second channel comprises a through hole or an elongated slot. The structure design is beneficial to simplifying the structure of the first channel and/or the second channel, reduces the difficulty of the production process and improves the production efficiency.

In a third aspect, embodiments of the present application provide a heat exchange system comprising a compressor, a throttling assembly, and a heat exchanger comprising a parallel flow heat exchanger as described in any of the preceding claims.

The first piece or the first component of the parallel flow heat exchanger can lengthen the flow length of the heat exchange medium, so that the heat exchange medium is uniformly distributed along the length direction of the first piece or the first component. Therefore, the heat exchange system adopting the parallel flow heat exchanger can reduce the distribution difference of heat exchange media on a plurality of heat exchange pipes, and improves the heat exchange efficiency of the heat exchange system.

It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the application.

[ description of the drawings ]

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

Fig. 1 is a schematic structural diagram of a parallel flow heat exchanger according to an embodiment of the present application.

Fig. 2 is a schematic view of a first member and a first tube in the parallel flow heat exchanger shown in fig. 1.

Fig. 3 is a cross-sectional view of the first member and the first tube of the parallel flow heat exchanger of fig. 1 taken along line A-A.

Fig. 4 is a schematic view of the structure of the first member in the parallel flow heat exchanger shown in fig. 3.

Fig. 5 is a schematic view of another first member and a first tube in the parallel flow heat exchanger shown in fig. 1.

Fig. 6 is another cross-sectional view of the first member and the first tube of the parallel flow heat exchanger of fig. 1 taken along line A-A.

Fig. 7 is a schematic view of a first member of the parallel flow heat exchanger of fig. 6.

Fig. 8 is a schematic view of another construction of the first member of the parallel flow heat exchanger shown in fig. 6.

Fig. 9 is a schematic view of still another construction of the first member of the parallel flow heat exchanger shown in fig. 6.

Fig. 10 is a schematic view of still another construction of the first member of the parallel flow heat exchanger shown in fig. 6.

Fig. 11 is a schematic view of still another first member and a first tube in the parallel flow heat exchanger shown in fig. 1.

Fig. 12 is a schematic view of still another first member and a first tube in the parallel flow heat exchanger shown in fig. 1.

Fig. 13 is a schematic view of still another first member and a first tube in the parallel flow heat exchanger shown in fig. 1.

Fig. 14 is a schematic structural diagram of a parallel flow heat exchanger according to an embodiment of the present disclosure.

Fig. 15 is a cross-sectional view of the first module of the parallel flow heat exchanger of fig. 14 taken along line B-B.

Fig. 16 is another cross-sectional view of the first module of the parallel flow heat exchanger of fig. 14 taken along line B-B.

Fig. 17 is yet another cross-sectional view of the first module of the parallel flow heat exchanger of fig. 14 taken along line B-B.

Fig. 18 is a schematic view showing a structure of a first channel provided on a first plate in the parallel flow heat exchanger shown in fig. 17.

Fig. 19 is a schematic view showing another structure of the first channel provided on the first plate in the parallel flow heat exchanger shown in fig. 17.

[ detailed description ] of the invention

For a better understanding of the technical solutions of the present application, embodiments of the present application are described in detail below with reference to the accompanying drawings.

It should be understood that the described embodiments are merely some, but not all, of the embodiments of the present application. All other embodiments, based on the embodiments herein, which would be apparent to one of ordinary skill in the art without making any inventive effort, are intended to be within the scope of the present application.

The terminology used in the embodiments of the application is for the purpose of describing particular embodiments only and is not intended to be limiting of the application. As used in this application and the appended claims, the singular forms "a," "an," and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise.

It should be understood that the term "and/or" as used herein is merely one relationship describing the association of the associated objects, meaning that there may be three relationships, e.g., a and/or B, may represent: a exists alone, A and B exist together, and B exists alone. In addition, the character "/" herein generally indicates that the front and rear associated objects are an "or" relationship.

The existing parallel flow heat exchanger generally comprises micro-channel flat tubes, radiating fins and a collecting tube. Collecting pipes are arranged at two ends of the micro-channel flat pipe and used for distributing and collecting heat exchange media. Corrugated or louvered radiating fins are arranged between two adjacent micro-channel flat tubes and used for enhancing the heat exchange efficiency of the heat exchanger and the air side.

In some applications, the refrigerant entering the parallel flow heat exchanger for heat exchange is usually in a two-phase flow state, the two-phase flow refrigerant is distributed in each micro-channel flat tube and each micro-channel in the flat tube, a state which is unfavorable for heat exchange performance can occur, and a distribution part is required to be designed to adjust the distribution of the two-phase flow refrigerant so as to avoid that the two-phase flow refrigerant directly enters a space of a collecting pipe for distribution, and the performance of the heat exchanger is affected.

In order to ensure even distribution of the refrigerant in each micro-channel flat tube, a metal flow guide tube is usually inserted into the collecting tube as a distribution component, through holes or through grooves are formed in the peripheral wall of the distribution component at intervals along the length direction of the distribution component, and the refrigerant can be uniformly distributed into each micro-channel flat tube through the through holes or the through grooves and then flows. However, the size, number and positions of the through holes or through grooves formed in the peripheral wall of the conventional distribution member are tested and adjusted according to different sizes of the parallel flow heat exchangers, so that the difficulty in producing the distribution pipe is increased, and the economic and time costs are increased.

In a first aspect, embodiments of the present application provide a parallel flow heat exchanger, which increases the flow length of the heat exchanger, and is beneficial to adjusting the distribution of heat exchange media, thereby improving the performance of the heat exchanger.

Referring to fig. 1 to 6, a parallel flow heat exchanger 100 includes a first tube 1, a second tube 5, a heat exchange tube, and a first member 2. Wherein the first tube 1 comprises a first tube wall 11, the first tube 1 having a first cavity 12, the wall surrounding the first cavity 12 comprising the first tube wall 11; the second tube 5 is arranged in parallel with the first tube 1, and the structures of the second tube 5 and the first tube 1 can be the same or different; the heat exchange tube comprises one or more micro-channel heat exchange tubes 3, the micro-channel heat exchange tubes 3 are directly connected or indirectly connected with the first tube 1, and the micro-channel heat exchange tubes 3 are directly connected or indirectly connected with the second tube 5; at least part of the first member 2 is located within the first chamber 12, the first member 2 comprising a second tube wall 21, the first member 2 having a second chamber 22, the wall surrounding the second chamber 22 comprising the second tube wall 21. Wherein, direct connection means that one pipe is not connected with the other pipe through the intermediate pipe, i.e. no intermediate pipe exists between the two pipes, and indirect connection means that one pipe is connected with the other pipe through the intermediate pipe, i.e. the intermediate pipe exists between the two pipes and is connected.

The second chamber 22 extends along the length direction of the first tube 1, the second chamber 22 comprises a first subchamber 221 and a second subchamber 222, the first subchamber 221 is indirectly communicated with the first chamber 12, the second subchamber 222 is directly communicated with the first chamber 12, and the first subchamber 221 is directly communicated with the second subchamber 222 or is indirectly communicated with the second subchamber 222. Wherein, the direct communication means that the liquid or the gas flows out from an outlet of one chamber and then directly flows into the other chamber; indirect communication refers to the flow of liquid or gas from the outlet of one chamber into another chamber after flowing through other structures such as other chambers or pipes.

The parallel flow heat exchanger 100 further comprises inlet and outlet pipes 6. The inlet and outlet pipe 6 is directly or indirectly connected with the first pipe 1; and/or the inlet and outlet pipe 6 is directly or indirectly connected with the second pipe 5. The inlet/outlet pipe 6 has an inlet/outlet passage which communicates directly or indirectly with the first subchamber 221.

The inlet and outlet pipe 6 is used for injecting heat exchange medium into the parallel flow heat exchanger 100, when the heat exchange medium needs to be injected into the parallel flow heat exchanger 100, the heat exchange medium sequentially passes through the inlet and outlet channel, the first subchamber 221, the second subchamber 222, the first chamber 12 and the channels on the micro-channel heat exchange pipe 3, so that heat exchange between the heat exchange medium and external medium (such as air) is realized.

By dividing the second cavity 22 in the first member 2 into the first subchamber 221 and the second subchamber 222, the flow length of the heat exchange medium in the first member 2 is prolonged, so that the heat exchange medium flows into the first cavity 12 after being uniformly distributed along the length direction of the first member 2, and the distribution of the heat exchange medium in the heat exchange tube is facilitated; meanwhile, as the flow length of the heat exchange medium in the first piece 2 is prolonged, the heat exchange medium can be fully mixed in the flowing process of the second cavity 22, so that the temperature distribution of the heat exchange medium along the length direction of the first piece 2 is uniform, and the heat exchange efficiency of the parallel flow heat exchanger 100 is improved. In addition, compared with the prior distribution component, the method of forming the through holes or the through grooves on the outer peripheral wall of the distribution component can effectively reduce the production difficulty of the prior distribution component and reduce the economic and time costs.

With continued reference to fig. 2-4, in some embodiments, the first member 2 includes a first channel 23 and a second channel 24, the first channel 23 communicates with the first subchamber 221 and the second subchamber 222, the second channel 24 communicates with the first chamber 12 and the second subchamber 222, and at least a portion of the first channel 23 and at least a portion of the second channel 24 extend along the length direction (i.e., the first direction D1) of the first tube 1. In a first plane perpendicular to the length direction of the first tube 1 (i.e. the first direction D1), the projection of the second tube wall 21 comprises at least a part of a spiral line and the projection of the second subchamber 222 comprises a plurality of rings. The heat exchange medium can flow along the spiral line in the second subchamber 222, so that the flow length of the heat exchange medium in the first piece 2 is prolonged, and the more the spiral turns of the spiral line are, the more uniformly the heat exchange medium is distributed along the length direction of the first piece 2.

Specifically, the first member 2 may be a hollow cylindrical structure formed by winding a plate material along a circumferential direction, without additionally providing a through hole or a through groove, thereby improving production efficiency. The hollow channel of the hollow cylinder structure in the middle forms a first subchamber 221, a second subchamber 222 is formed along the hollow cylinder structure around the clearance of the hollow cylinder structure in the spiral direction of the axis, and the first subchamber 221 and the second subchamber 222 are directly communicated.

With continued reference to fig. 5 and 6, in some embodiments, the second tube wall 21 includes a first sub-wall 211 and a second sub-wall 212, the first sub-wall 211 and the second sub-wall 212 extending in a length direction of the first tube 1, the first sub-wall 211 and the second sub-wall 212 having a thickness. The first sub-wall 211 has a first passage 25, the first passage 25 communicating the first sub-chamber 221 and the second sub-chamber 222. The second sub-wall 212 has a second passageway 26, the second passageway 26 communicating the second sub-chamber 222 with the first chamber 12. In a first plane perpendicular to the length direction of the first tube 1, the projection of the first sub-wall 211 comprises a first circular arc, the projection of the second sub-wall 212 comprises a plurality of second circular arcs, the circumference of at least one second circular arc being larger than the circumference of the first circular arc, any one of the second circular arcs comprising the projection of at least one second channel 26.

Specifically, the second sub-wall 212 is sleeved on the outer periphery of the first sub-wall 211 along the radial direction, and the second sub-wall 212 includes a plurality of third sub-walls 2121 distributed at intervals along the radial direction of the first member 2, and a second channel is provided on any one of the third sub-walls 2121. Wherein, in the radial direction of the first member 2, the third sub-wall 2121 located at the outermost side (i.e., the third sub-wall 2121 closest to the first sub-wall 211) surrounds the second sub-chamber 222, and the remaining third sub-walls 2121 surround the third sub-chambers 223, respectively, and the first sub-chamber 221 communicates with the second sub-chamber 222 through one or more third sub-chambers 223. The heat exchange medium flows through the first sub-chamber 221, the third sub-chamber 223, the second sub-chamber 222 and the first chamber 12 in sequence, thereby lengthening the flow path length of the heat exchange medium in the first member 2.

The number of third sub-walls 2121 may be one, two, three or any other number, and the greater the number of third sub-walls 2121, the more uniform the heat exchange medium is distributed along the length direction of the first member 2, which is not limited herein. For example, the number of third sub-walls 2121 may be one, the first sub-chamber 221 being in direct communication with the second sub-chamber 222; the number of the third sub-walls 2121 may be two, and the first sub-chamber 221 communicates with the second sub-chamber 222 through one third sub-chamber 223; the number of the third sub-walls 2121 may be three, and the first sub-chamber 221 may communicate with the second sub-chamber 222 through two third sub-chambers 223 in sequence.

It will be appreciated that the first member 2 may take on a multi-layered sleeve structure, thereby dividing the second subchamber 222 into a plurality of subchambers, simplifying the production process of the first member 2.

In the first plane, the projection of the second sub-wall 212 comprises at least three second arcs comprising one or more radii, at least one radius of one second arc being different from at least one radius of another second arc. In the radial direction of the first tube 1, the maximum difference in radius values between every two adjacent second arcs is inversely proportional to the distance from any one of the second arcs to the first arc.

Specifically, the second arc may be a regular arc, that is, the third sub-wall 2121 surrounds and forms a circular tube-like structure; the second circular arc may also comprise a plurality of circular arc segments of different radii, i.e. the third sub-wall 2121 surrounds an irregular tubular structure. The maximum width of the gap formed between two adjacent third sub-walls 2121 in the radial direction of the first member 2 away from the first sub-wall 211 is inversely proportional to the distance from the third sub-wall 2121 located inside or the third sub-wall 2121 located outside to the first sub-wall 211. In this way, the first member 2 is more suitable for the state change of the heat exchange medium in the flowing process, and the improvement of the heat exchange performance is facilitated.

It will be appreciated that the maximum difference in radius values between two adjacent second arcs may not be proportional to the distance between any one of the second arcs to the first arc, as long as the maximum difference in radius values between two adjacent second arcs is gradually decreased in a direction away from the first sub-wall 211 in the radial direction of the first member 2.

Referring to fig. 7 to 9, in some embodiments, the first channel 25 and/or the second channel 26 may include a plurality of through holes disposed at intervals.

Specifically, the first sub-wall 211 includes one or more first through holes 251, the first through holes 251 penetrating the first sub-wall 211, the first through holes 251 communicating the first sub-chamber 221 and the second sub-chamber 222. The second sub-wall 212 includes a plurality of second through holes penetrating the second sub-wall 212, at least a portion of the second through holes communicating the second sub-cavity 222 with the first cavity 12, and the first through holes 251 communicating indirectly with the second through holes.

With continued reference to fig. 7, in some embodiments, the first channel 25 includes a plurality of first through holes 251 disposed on the first sub-wall 211 at intervals along the length direction (the first direction D1) of the first member 2.

With continued reference to fig. 8, in some embodiments, the first channel 25 includes at least two parallel rows of through holes, and any row of through holes includes a plurality of first through holes 251 disposed on the first sub-wall 211 at intervals along the length direction (the first direction D1) of the first member 2. The sizes of the apertures of the first through holes 251 in the adjacent two rows of through hole groups may be the same or different, and are not limited herein.

With continued reference to fig. 9, in some embodiments, the first channel 25 includes a plurality of first through holes 251 disposed on the first sub-wall 211 in a spiral along the axis L of the first member 2. Wherein the axis L extends in the length direction (first direction D1) of the first member 2.

Similarly, the second channel 26 also includes a plurality of second through holes provided on the second sub-wall 212 at intervals along the length direction (first direction D1) of the first member 2; alternatively, the second passage 26 also includes at least two parallel rows of through-hole groups, and any one row of through-hole groups includes a plurality of second through-holes provided on the second sub-wall 212 at intervals along the length direction (first direction D1) of the first member 2; alternatively, the second channel 26 also comprises a plurality of second through holes arranged in a spiral on the second sub-wall 212 along the axis L of the first piece 2.

In the first plane, the projected center of the at least one first through hole 251 and the projected center of the at least one second through hole are collinear.

Specifically, the second through hole formed in the third sub-wall 2121 located at the innermost side is disposed at an angle of 180 ° with the first through hole 251 formed in the first sub-wall 211, and the second through holes formed in the two adjacent third sub-walls 2121 are also disposed at an angle of 180 °. In this way, the heat exchange media flowing out from the first through hole 251 and dispersed into two flows respectively flow through the flow length of the same length, and then are collected at the second through hole at the same time, so that the heat exchange media are further ensured to flow into the first cavity 12 through the second through hole after being uniformly distributed along the length direction of the first member 2.

The first sub-wall 211 has a smaller number of first through holes 251 than the second sub-wall 212 has; and/or, the sum of the flow areas of the first through holes 251 is smaller than the sum of the flow areas of the second through holes.

Specifically, the number of the first through holes 251 formed in the first sub-wall 211 is smaller than the number of the second through holes formed in the third sub-wall 2121 located at the innermost side, and the number of the second through holes formed in the third sub-wall 2121 located at the inner side is smaller than the number of the second through holes formed in the third sub-wall 2121 located at the outer side in the direction away from the first sub-wall 211 in the radial direction of the first member 2; or, the sum of the flow areas of the first through holes 251 formed in the first sub-wall 211 is smaller than the sum of the flow areas of the second through holes formed in the third sub-wall 2121 located at the innermost side, and the sum of the flow areas of the second through holes formed in the third sub-wall 2121 located at the inner side is smaller than the sum of the flow areas of the second through holes formed in the third sub-wall 2121 located at the outer side in the direction away from the first sub-wall 211 in the radial direction of the first member 2. This allows the flow of heat exchange medium from the second through holes into the first chamber 12 to be accelerated, thereby avoiding accumulation of heat exchange medium in the first member 2, reducing the filling amount of heat exchange medium, and reducing the distribution difference of heat exchange medium on the plurality of heat exchange tubes between two adjacent second through holes.

Referring to fig. 10, in some embodiments, the first channel 25 and/or the second channel 26 may be elongated slots disposed along the length direction (the first direction D1) of the first member 2, so that the production process of the first member 2 may be simplified instead of forming the first through hole 251 or the second through hole, and further the production efficiency may be improved.

The flow area of the first long groove 252 formed in the first sub-wall 211 is smaller than the flow area of the second long groove formed in the third sub-wall 2121 located at the innermost side, and the flow area of the second long groove formed in the third sub-wall 2121 located at the inner side is smaller than the flow area of the second long groove formed in the third sub-wall 2121 located at the outer side in the direction of the first member 2 away from the first sub-wall 211. This allows the flow of heat exchange medium from the second channel 26 out of the second subchamber 222 to be accelerated when the heat exchange medium flows from the second channel 26 into the first chamber 12, thereby avoiding accumulation of heat exchange medium in the first member 2 and thus reducing the filling amount of heat exchange medium.

It can be appreciated that the first channel 25 formed on the first sub-wall 211 may be a first long groove 252, and the second channel 26 formed on some or all of the third sub-walls 2121 may be a second long groove; alternatively, the first channel 25 formed on the first sub-wall 211 is the first long groove 252, and the second channels 26 formed on some or all of the third sub-walls 2121 may be a plurality of second through holes; alternatively, the first channels 25 formed on the first sub-wall 211 may be a plurality of first through holes 251, and the second channels 26 formed on some or all of the third sub-walls 2121 may be second elongated slots; alternatively, the first channels 25 formed on the first sub-wall 211 may be a plurality of first through holes 251, and the second channels 26 formed on some or all of the third sub-walls 2121 may be second through holes.

Referring to fig. 11, in some embodiments, in the first plane, the projection of the second sub-wall 212 includes a second arc, the second arc includes projections of the plurality of second through holes 261, and the number of second through holes 261 is greater than the number of first through holes 251.

Specifically, the second sub-wall 212 is sleeved on the outer periphery of the first sub-wall 211 along the radial direction thereof, so that the first member 2 presents an inner and outer sleeve structure, which is beneficial to ensuring that the heat exchange medium is evenly distributed along the length direction of the first member 2 and then redistributed to each heat exchange tube 3, thereby reducing the distribution difference of the heat exchange medium on the plurality of heat exchange tubes 3.

The ratio of the number of first through holes 251 to the number of second through holes 261 is less than or equal to 1/2. In this way, the heat exchange medium flows into the first tube 1 after being uniformly distributed along the length direction of the first member 2, and meanwhile, the difference of distribution of the heat exchange medium on each heat exchange tube 3 is reduced.

Specifically, the ratio of the number of the first through holes 251 to the number of the second through holes 261 may be any other value such as 1/2, 1/3, 1/4, 1/5, etc., so long as the number of the second through holes 261 is greater than the number of the first through holes 251, which is not limited herein. In the embodiment of the present application, the ratio of the number of the first through holes 251 to the number of the second through holes 261 may be 1/2.

Referring to fig. 12 and 13, in some embodiments, in the first plane, the projection of the second sub-wall 212 includes two second arcs, wherein, in the radial direction of the first pipe 1, one second arc near the first arc includes the projection of a plurality of second through holes (not shown in the drawings), and the number of the second through holes is greater than the number of the first through holes 251, and the other second arc far from the first arc includes the projection of at least one elongated slot 262.

Specifically, the second sub-wall 212 is sleeved on the outer periphery of the first sub-wall 211 along the radial direction thereof, and the second sub-wall 212 includes two third sub-walls 2121 distributed at intervals along the radial direction of the first member 2, so that the first member 2 presents an inner and outer three-layer sleeve structure, wherein a plurality of second through holes are formed in the third sub-wall 2121 located at the innermost side, and at least one long groove 262 is formed in the third sub-wall located at the outermost side.

The second through holes formed in the third sub-wall 2121 and the first through holes 251 formed in the first sub-wall 211 are located at the innermost side, so that the heat exchange medium is distributed uniformly along the length direction of the first member 2 and then redistributed to the heat exchange tubes 3, and the mixing of the gas-liquid two-phase heat exchange medium is facilitated, and the distribution uniformity of the heat exchange medium in the plurality of heat exchange tubes 3 is further improved. The ratio of the number of the first through holes 251 to the number of the second through holes is the same as that of the previous embodiment, and will not be described again.

In addition, the third sub-wall 2121 positioned at the outermost side is provided with the long groove 262, which is favorable for reducing the resistance of the heat exchange medium in the flowing process, reducing the influence on the side pressure of the heat exchange medium and improving the heat exchange performance; meanwhile, the long groove 262 has a larger flow area, so that the difference of distribution of heat exchange media on the plurality of heat exchange tubes 3 is reduced.

In a second aspect, the embodiments of the present application also provide another parallel flow heat exchanger, which can also effectively reduce the difficulty in producing the distribution pipe provided in the existing parallel flow heat exchanger, so as to reduce the economic and time costs.

Referring to fig. 14 to 17, the parallel flow heat exchanger 100 includes a first module 4 and at least one heat exchange tube 3, and the first module 4 is directly or indirectly connected to the heat exchange tube 3. Wherein the heat exchange tube 3 has a plurality of channels extending in a length direction thereof; the first component 4 comprises a first tube wall 41, the first component 4 has a first cavity 43, the wall surrounding the first cavity 43 comprises the first tube wall 41, the first component 4 further comprises a first plate 42a and a second plate 42b, the first plate 42a and the second plate 42b extend along the length direction of the first component 4, at least part of the first plate 42a and at least part of the second plate 42b are positioned in the first cavity 43, the first plate 42a and the second plate 42b are arranged along the width direction or the height direction of the first component 4, the first plate 42a is connected with the inner wall of the first tube wall 41, and the second plate 42b is connected with the inner wall of the first tube wall 41.

The first chamber 43 includes a first sub-chamber 431, a second sub-chamber 432 and a third sub-chamber 433, and the third sub-chamber 433 is in direct communication with the plurality of passages of the heat exchange tube 3. The first plate 42a includes a first channel 44 and the second plate 42b includes a second channel 45, the first channel 44 communicating with the first sub-chamber 431 and the second sub-chamber 432, the second channel 45 communicating with the second sub-chamber 432 and the third sub-chamber 433, the first channel 44 and the second channel 45 indirectly communicating.

The parallel flow heat exchanger 100 further comprises a second module 7, the second module 7 being arranged in parallel with the first module 4, the second module 7 being of the same or different construction than the first module 4.

The parallel flow heat exchanger 100 further comprises an inlet and outlet pipe 8, wherein the inlet and outlet pipe 8 is directly or indirectly connected with the first component 4, and the inlet and outlet pipe 8 is provided with an inlet and outlet channel which is directly or indirectly communicated with the first subchamber 431; and/or the inlet and outlet pipe 8 is directly or indirectly connected with the second component 7.

The inlet and outlet pipe 8 is used for injecting heat exchange medium into the parallel flow heat exchanger 100, when the heat exchange medium needs to be injected into the parallel flow heat exchanger 100, the heat exchange medium flows into the heat exchange pipe 3 through the inlet and outlet channel, the first subchamber 431, the second subchamber 432, the third subchamber 433 and a plurality of channels on the heat exchange pipe 3 in sequence, so that heat exchange between the heat exchange medium and external media (such as air) is realized.

By arranging the first plate 42a and the second plate 42b in the first cavity 43, the first cavity 43 can be divided into a first subchamber 431, a second subchamber 432 and a third subchamber 433, so that the flow length of the heat exchange medium in the first component 4 is prolonged, the heat exchange medium is uniformly distributed along the length direction of the first component 4 and then flows into a plurality of channels of the heat exchange tube 3, and the distribution of the heat exchange medium in the heat exchange tube is facilitated; meanwhile, as the flow length of the heat exchange medium in the first component 4 is prolonged, the heat exchange medium can be fully mixed in the flowing process in the first cavity 43, so that the temperature distribution of the heat exchange medium along the length direction of the first component 4 is uniform, and the heat exchange efficiency of the parallel flow heat exchanger 100 is improved. In addition, compared with the prior distribution component, the method of forming the through holes or the through grooves on the outer peripheral wall of the distribution component can effectively reduce the production difficulty of the prior distribution component and reduce the economic and time costs.

The first pipe wall 41 includes a first sub-wall 411 and a second sub-wall 412 disposed opposite to each other in the width direction (second direction D2) of the first component 4, a third sub-wall 413 and a fourth sub-wall 414 disposed opposite to each other in the height direction (third direction D3) of the first component 4, and a fifth side wall (not shown) and a sixth side wall (not shown) disposed opposite to each other in the length direction (first direction D1) of the first component 4.

With continued reference to fig. 15, in some embodiments, the first plate 42a and the second plate 42b are disposed in the first cavity 43 at intervals along the height direction (the third direction D3) of the first component 4, so as to divide the first cavity 43 into a first sub-cavity 431, a second sub-cavity 432 and a third sub-cavity 433 sequentially along the height direction (the third direction D3) of the first component 4.

Specifically, the first plate 42a and the second plate 42b may be connected to any three of the first sub-wall 411, the second sub-wall 412, the fifth sub-wall or the sixth sub-wall, respectively, and a gap between a sub-wall of the first sub-wall 411, the second sub-wall 412, the fifth sub-wall or the sixth sub-wall, which is not connected to the first plate 42a, and the first plate 42a forms a first channel 44, and a gap between a sub-wall of the first sub-wall 411, the second sub-wall 412, the fifth sub-wall or the sixth sub-wall, which is not connected to the second plate 42b, and the second plate 42b forms a second channel 45.

At least one third plate 42c is further disposed in the first cavity 43, and any one of the third plates 42c is disposed between the first plate 42a and the second plate 42b to divide the second sub-cavity 432 into a plurality of sub-chambers along the height direction (third direction D3) of the first component 4, and any one of the third plates 42c may be connected to any three of the first sub-wall 411, the second sub-wall 412, the fifth sub-wall or the sixth sub-wall, and a gap between the third plate 42c and a sub-wall of the first sub-wall 411, the second sub-wall 412, the fifth sub-wall or the sixth sub-wall, which is not connected to the third plate 42c, forms a third passage 46 to communicate with each of the sub-chambers in the second sub-cavity 432.

The number of the third plates 42c may be one, two, three or any other number, and the greater the number of the third plates 42c, the greater the number of subchambers formed by separating the second subchamber 432, the greater the number of detouring flows of the heat exchange medium in the second subchamber 432, so that the heat exchange medium is uniformly distributed along the length direction (the first direction D1) of the first assembly 4, which is not limited herein.

When the number of the third plates 42c is one, in the second plane perpendicular to the height direction (third direction D3) of the first member 4, the projection of the first passage 44 formed between the first plate 42a and the first tube wall 41 does not overlap with the projection of the third passage 46 formed between the third plate 42c and the first tube wall 41 and is set at an angle of 180 °, while the projection of the second passage 45 formed between the second plate 42b and the first tube wall 41 also does not overlap with the projection of the third passage 46 formed between the third plate 42c and the first tube wall 41 and is set at an angle of 180 °.

When the number of the third plates 42c is plural, in the second plane perpendicular to the height direction (third direction D3) of the first member 4, the projection of the first passage 44 formed between the first plate 42a and the first tube wall 41 does not overlap with the projection of the third passage 46 formed between the third plate 42c located at the lowermost side and the first tube wall 41 and is disposed at an angle of 180 °, the projections of the third passages 46 formed between the adjacent two third plates 42c and the first tube wall 41 do not overlap with each other and are disposed at an angle of 180 °, and the projection of the second passage 45 formed between the second plate 42b and the first tube wall 41 does not overlap with the projection of the third passage 46 formed between the third plate 42c located at the uppermost side and the first tube wall 41 and is disposed at an angle of 180 °.

With continued reference to fig. 16, in some embodiments, the first plate 42a and the second plate 42b are disposed in the first cavity 43 at intervals along the width direction (the second direction D2) of the first component 4, so as to divide the first cavity 43 into a first sub-cavity 431, a second sub-cavity 432 and a third sub-cavity 433 along the width direction (the second direction D2) of the first component 4 in sequence.

Specifically, the first plate 42a and the second plate 42b may be connected to any three of the third sub-wall 413, the fourth sub-wall 414, the fifth sub-wall, or the sixth sub-wall, respectively, and a gap formed between a sub-wall of the third sub-wall 413, the fourth sub-wall 414, the fifth sub-wall, or the sixth sub-wall, which is not connected to the first plate 42a, and the first plate 42a forms the first channel 44, and a gap between a sub-wall of the third sub-wall 413, the fourth sub-wall 414, the fifth sub-wall, or the sixth sub-wall, which is not connected to the second plate 42b, and the second plate 42b forms the second channel 45.

At least one third plate 42c is further provided in the first chamber 43, and any one of the third plates 42c is located between the first plate 42a and the second plate 42b to partition the second sub-chamber 432 into a plurality of sub-chambers in the width direction (second direction D2) of the first assembly 4, and any one of the third plates 42c may be connected to any three of the third sub-wall 413, the fourth sub-wall 414, the fifth sub-wall or the sixth sub-wall, and a gap between the third sub-wall 413, the fourth sub-wall 414, the fifth sub-wall or the sixth sub-wall, which is not connected to the third plate 42c, and the third plate 42c forms the third passage 46.

The number of the third plates 42c may be one, two, three or any other number, and the greater the number of the third plates 42c, the greater the number of subchambers formed by separating the second subchamber 432, the greater the number of detouring flows of the heat exchange medium in the second subchamber 432, so that the heat exchange medium is uniformly distributed along the length direction (the first direction D1) of the first assembly 4, which is not limited herein.

When the number of the third plates 42c is one, in the third plane perpendicular to the width direction (second direction D2) of the first member 4, the projection of the first passage 44 formed between the first plate 42a and the first tube wall 41 does not overlap with the projection of the third passage 46 formed between the third plate 42c and the first tube wall 41 and is set at an angle of 180 °, while the projection of the second passage 45 formed between the second plate 42b and the first tube wall 41 also does not overlap with the projection of the third passage 46 formed between the third plate 42c and the first tube wall 41 and is set at an angle of 180 °.

When the number of the third plates 42c is plural, in the third plane perpendicular to the width direction (second direction D2) of the first member 4, the projection of the first passage 44 formed between the first plate 42a and the first tube wall 41 does not overlap with the projection of the third passage 46 formed between the third plate 42c located on the far right side and the first tube wall 41 and is disposed at an angle of 180 °, and the projection of the third passage 46 formed between the adjacent two third plates 42c and the first tube wall 41 does not overlap with the projection of the second passage 45 formed between the second plate 42b and the first tube wall 41 and is disposed at an angle of 180 ° with the projection of the third passage 46 formed between the third plate 42c located on the far left side and the first tube wall 41.

The first, second and third plates 42a, 42b and 42c are disposed at intervals along the width direction (second direction D2) of the first module 4, and the height dimension of the first module 4 can be reduced as compared to the arrangement of the first, second and third plates 42a, 42b and 42c along the height direction (third direction D3) of the first module 4, thereby adapting the parallel flow heat exchanger 100 to a mounting space having a smaller height.

With continued reference to fig. 17, in some embodiments, the first plate 42a and the second plate 42b are disposed in the first cavity 43 at intervals along the height direction (the third direction D3) of the first component 4, so as to divide the first cavity 43 into a first sub-cavity 431, a second sub-cavity 432 and a third sub-cavity 433 sequentially along the height direction (the third direction D3) of the first component 4. The first plate 42a and the second plate 42b may be connected to the first sub-wall 411, the second sub-wall 412, the fifth sub-wall and the sixth sub-wall, respectively, the first plate 42a is provided with a first channel 44 communicating the first sub-chamber 431 and the second sub-chamber 432, and the second plate 42b is provided with a second channel 45 communicating the second sub-chamber 432 and the third sub-chamber 433.

At least one third plate 42c is further disposed in the first cavity 43, any one of the third plates 42c is disposed between the first plate 42a and the second plate 42b to divide the second sub-cavity 432 into a plurality of sub-cavities along the height direction (third direction D3) of the first component 4, and any one of the third plates 42c may be connected to the first sub-wall 411, the second sub-wall 412, the fifth sub-wall and the sixth sub-wall, and a third channel 46 communicating with each of the sub-cavities in the second sub-cavity 432 is disposed on the third plate 42 c.

The number of the third plates 42c may be one, two, three or any other number, and the greater the number of the third plates 42c, the greater the number of subchambers formed by separating the second subchamber 432, the greater the number of detouring flows of the heat exchange medium in the second subchamber 432, so that the heat exchange medium is uniformly distributed along the length direction (the first direction D1) of the first assembly 4, which is not limited herein.

When the number of the third plates 42c is one, in the second plane perpendicular to the height direction (third direction D3) of the first member 4, the projection of the first passage 44 provided on the first plate 42a does not overlap with the projection of the third passage 46 provided on the third plate 42c and is set at an angle of 180 °, while the projection of the second passage 45 provided on the second plate 42b also does not overlap with the projection of the third passage 46 provided on the third plate 42c and is set at an angle of 180 °.

When the number of the third plates 42c is plural, in the second plane perpendicular to the height direction (third direction D3) of the first member 4, the projections of the first passages 44 provided on the first plate 42a do not overlap with the projections of the third passages 46 provided on the third plate 42c located at the lowermost side and are disposed at an angle of 180 °, the projections of the third passages 46 provided on the adjacent two third plates 42c do not overlap with each other and are disposed at an angle of 180 °, and the projections of the second passages 45 provided on the second plate 42b do not overlap with the projections of the third passages 46 provided on the third plate 42c located at the uppermost side and are disposed at an angle of 180 °.

It will be appreciated that the first plate 42a, the second plate 42b and the third plate 42c may also be disposed at intervals along the width direction (the second direction D2) of the first module 4, and the first plate 42a, the second plate 42b and the third plate 42c may be connected with the third sub-wall 413, the fourth sub-wall 414, the fifth sub-wall and the sixth sub-wall, respectively, to reduce the height dimension of the first module 4, thereby adapting the parallel flow heat exchanger 100 to a mounting space with a smaller height.

The first channel 44 includes a through hole or slot; and/or, the second channel 45 comprises a through hole or an elongated slot, which is beneficial to simplifying the structure of the first channel 44 and/or the second channel 45, reducing the difficulty of the production process and improving the production efficiency.

Referring to fig. 18, in some embodiments, the first channel 44 and the second channel 45 may include a plurality of through holes spaced along the length direction (the first direction D1) of the first component 4.

Specifically, the number of through holes provided on the first plate 42a is smaller than the number of through holes provided on the second plate 42 b; and/or the sum of the flow areas of the through holes provided on the first plate 42a is smaller than the sum of the flow areas of the through holes provided on the second plate 42 b. In this way, the sum of the flow areas of the first channels 44 is smaller than the sum of the flow areas of the second channels 45, so that the heat exchange medium in the second subchamber 432 can be accelerated to flow from the second channels 45 into the third subchamber 433 and finally flow into the channels of the heat exchange tube 3, thereby avoiding accumulation of the heat exchange medium in the first component 4 and further reducing the filling amount of the heat exchange medium.

Referring to fig. 19, in some embodiments, the first channel 44 and the second channel 45 may also be elongated slots disposed along the length direction (the first direction D1) of the first component 4, so that the production process of the first component 4 is simplified instead of the through holes, and the production efficiency is improved.

The flow area of the elongated slots formed in the first plate 42a is smaller than the flow area of the elongated slots formed in the second plate 42b, so that when the heat exchange medium flows into the first chamber 43 from the second channel 45, the heat exchange medium can be accelerated to flow out of the second subchamber 432 from the second channel 45, thereby avoiding accumulation of the heat exchange medium in the first member and further reducing the filling amount of the heat exchange medium.

It will be appreciated that the first channel 44 formed in the first plate 42a may be a long slot, and the second channel 45 formed in the second plate 42b may be a long slot; alternatively, the first channel 44 formed on the first plate 42a is a long slot, and the second channel 45 formed on the second plate 42b may be a plurality of through holes; alternatively, the first channel 44 formed on the first plate 42a may be a plurality of through holes, and the second channel 45 formed on the second plate 42b may be an elongated slot; alternatively, the first passages 44 formed in the first plate 42a may be a plurality of through holes, and the second passages 45 formed in the second plate 42b may be a plurality of through holes.

The sum of the flow areas of the first channels 44 is smaller than the sum of the flow areas of the second channels 45. The heat exchange medium in the second subchamber 432 can be accelerated to flow into the third subchamber 433 from the second channel 45 and finally flow into the channels of the heat exchange tube 3 by the structural design, so that accumulation of the heat exchange medium in the first component 4 is avoided, and the filling amount of the heat exchange medium is reduced.

The third passage 46 may include a plurality of through holes spaced apart along the length direction (first direction D1) of the first member 4; alternatively, the third passage 46 may be an elongated groove provided along the longitudinal direction (first direction D1) of the first module 4. Illustratively, in the height direction (third direction D3) of the first module 4, in the adjacent two third plates 42c, the flow area of the third passage 46 opened on the third plate 42c located on the upper side is larger than the flow area of the third passage 46 opened on the third plate 42c located on the lower side, and the flow area of the third passage 46 opened on any one of the third plates 42c is between the flow area of the first passage 44 opened on the first plate 42a and the flow area of the second passage 45 opened on the second plate 42 b.

In a third aspect, an embodiment of the present application further provides a heat exchange system, including a compressor, a throttling component (such as a throttling valve) and a heat exchanger, where the heat exchanger includes the aforementioned parallel flow heat exchanger 100, and the heat exchange system using the parallel flow heat exchanger 100 is beneficial to improving heat exchange performance of the heat exchange system.

The parallel flow heat exchanger 100 disclosed in the embodiments of the present application may be used for, but not limited to, a heat exchange system for an air conditioner for a vehicle, a home air conditioner, an industrial air conditioner, and the like.

Because the first piece 2 or the first component 4 of the parallel flow heat exchanger 100 can lengthen the flow path length of the heat exchange medium, the heat exchange medium is uniformly distributed along the length direction of the first piece 2 or the first component 4. Therefore, the heat exchange system adopting the parallel flow heat exchanger 100 can reduce the distribution difference of the heat exchange medium on the plurality of heat exchange pipes 3, and improves the heat exchange efficiency of the heat exchange system.

The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather to enable any modification, equivalent replacement, improvement or the like to be made within the spirit and principles of the invention.

Claims (13)

1. A parallel flow heat exchanger comprising:

a first tube comprising a first tube wall, the first tube having a first cavity, a wall surrounding the first cavity comprising the first tube wall;

a second pipe arranged in parallel with the first pipe;

the heat exchange tube comprises a micro-channel heat exchange tube, the micro-channel heat exchange tube is directly connected or indirectly connected with the first tube, and the micro-channel heat exchange tube is directly connected or indirectly connected with the second tube;

The first piece, at least part first piece is located first intracavity, first piece includes the second pipe wall, first piece has the second chamber, around the wall in second chamber includes the second pipe wall, the second chamber is followed the length direction of first pipe extends, the second chamber includes first subchamber and second subchamber, first subchamber with first chamber indirect communication, the second subchamber with first chamber direct communication, first subchamber with second subchamber direct communication or indirect communication.

2. The parallel flow heat exchanger of claim 1 wherein the first member comprises a first port and a second port, the first port communicating with the first subchamber and the second subchamber, the second port communicating with the first chamber and the second subchamber, at least a portion of the first port and at least a portion of the second port extending along a length of the first tube;

in a first plane perpendicular to the length direction of the first tube, the projection of the second tube wall comprises at least a part of a spiral line, and the projection of the second subchamber comprises a plurality of circular rings.

3. The parallel flow heat exchanger of claim 1 wherein the second tube wall comprises a first sub-wall and a second sub-wall, the first sub-wall and the second sub-wall extending in a length direction of the first tube, the first sub-wall and the second sub-wall having a thickness;

The first sub-wall comprises one or more first through holes, the first through holes penetrate through the first sub-wall, and the first through holes are communicated with the first sub-cavity and the second sub-cavity;

the second sub-wall comprises a plurality of second through holes, the second through holes penetrate through the second sub-wall, at least part of the second through holes are communicated with the second sub-cavity and the first cavity, and the first through holes are indirectly communicated with the second through holes;

in a first plane perpendicular to the length direction of the first tube, the projection of the first sub-wall comprises a first circular arc, the projection of the second sub-wall comprises one or more second circular arcs, and the perimeter of at least one of the second circular arcs is larger than the perimeter of the first circular arc.

4. A parallel flow heat exchanger as set forth in claim 3 wherein the projected centers of at least one of said first through holes and at least one of said second through holes are collinear in said first plane.

5. The parallel flow heat exchanger of claim 3 or 4 wherein, in the first plane, the projection of the second sub-wall comprises at least three of the second arcs, the second arcs comprising one or more radii, at least one of the radii of one of the second arcs being different from at least one of the radii of the other of the second arcs;

The maximum difference in the radius values between every two adjacent second arcs in the radial direction of the first pipe is inversely proportional to the distance from any one of the second arcs to the first arc.

6. The parallel flow heat exchanger of claim 3 or 4 wherein the first sub-wall has a smaller number of the first through holes than the second sub-wall has the second through holes;

and/or the sum of the flow areas of the first through holes is smaller than the sum of the flow areas of the second through holes.

7. A parallel flow heat exchanger as set forth in claim 3 wherein in said first plane the projection of said second sub-wall comprises one of said second arcs comprising a plurality of projections of said second through holes, and the number of said second through holes is greater than the number of said first through holes.

8. A parallel flow heat exchanger as claimed in claim 3 wherein in said first plane the projection of said second sub-wall comprises two of said second arcs, wherein in the radial direction of said first tube one of said second arcs adjacent to said first arc comprises a projection of a plurality of said second through holes, and the number of said second through holes is greater than the number of said first through holes, and the other of said second arcs remote from said first arc comprises a projection of at least one elongated slot.

9. The parallel flow heat exchanger of claim 7 or 8 wherein the ratio of the number of first through holes to the number of second through holes is less than or equal to 1/2.

10. A parallel flow heat exchanger comprising:

a heat exchange tube having a plurality of channels extending along a length direction thereof;

the first assembly is directly connected or indirectly connected with the heat exchange tube, the first assembly comprises a first tube wall, the first assembly is provided with a first cavity, the wall surrounding the first cavity comprises the first tube wall, the first assembly further comprises a first plate and a second plate, the first plate and the second plate extend along the length direction of the first assembly, at least part of the first plate and at least part of the second plate are positioned in the first cavity, the first plate and the second plate are arranged along the width direction or the height direction of the first assembly, the first plate is connected with the inner wall of the first tube wall, the second plate is connected with the inner wall of the first tube wall, the first cavity comprises a first subchamber, a second subchamber and a third subchamber, and a plurality of channels of the third subchamber and the heat exchange tube are directly communicated;

The first plate includes a first channel, the second plate includes a second channel, the first channel communicates with the first subchamber and the second subchamber, the second channel communicates with the second subchamber and the third subchamber, and the first channel communicates with the second channel indirectly.

11. The parallel flow heat exchanger of claim 10 wherein the sum of the flow areas of the first channels is less than the sum of the flow areas of the second channels.

12. The parallel flow heat exchanger of claim 10 or 11 wherein the first channel comprises a through hole or an elongated slot; and/or the second channel comprises a through hole or an elongated slot.

13. A heat exchange system comprising a compressor, a throttling assembly and a heat exchanger comprising a parallel flow heat exchanger according to any of claims 1-12.

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