CN216482483U

CN216482483U - Flow collecting structure, micro-channel heat exchanger and air conditioner

Info

Publication number: CN216482483U
Application number: CN202121451888.2U
Authority: CN
Inventors: 何哲旺
Original assignee: GD Midea Air Conditioning Equipment Co Ltd; Handan Midea Air Conditioning Equipment Co Ltd
Current assignee: GD Midea Air Conditioning Equipment Co Ltd; Handan Midea Air Conditioning Equipment Co Ltd
Priority date: 2021-06-28
Filing date: 2021-06-28
Publication date: 2022-05-10
Anticipated expiration: 2031-06-28

Abstract

The utility model discloses a flow collecting structure, a micro-channel heat exchanger and an air conditioner, wherein the flow collecting structure comprises a substrate, a plurality of channels communicated with pipelines in heat exchange fins are arranged on the substrate, the channels extend along a first direction, and the channels are distributed at intervals along a second direction; the base plate is provided with a fluid passage for leading fluid into the channels, the fluid passage comprises a first pore passage, a second pore passage and a third pore passage, and the first pore passage and the second pore passage are respectively arranged at two ends of the channels in the first direction and are communicated with the channels; one end of the first duct in the second direction is set as a first end part, and one end of the second duct in the second direction, which is far away from the first end part, is set as a second end part; one end of the third pore canal extends to one end surface of the base plate, and the other end is connected with the first end part and the second end part. The microchannel heat exchanger includes heat exchanger fins and a flow collection structure. The air conditioner includes a microchannel heat exchanger. The technical scheme provided by the utility model aims to solve the technical problem of uneven distribution of the existing fluid.

Description

Flow collecting structure, micro-channel heat exchanger and air conditioner

Technical Field

The utility model relates to the field of electrical equipment, in particular to a current collecting structure, a micro-channel heat exchanger and an air conditioner.

Background

The air conditioner heat exchanger experiences the traditional tube fin heat exchanger and the novel micro-channel heat exchanger, and the development of the next generation air conditioner heat exchanger to the superfine pipe diameter is an important direction along with the continuous increase of the requirements on high energy efficiency and environment-friendly air conditioners. At present, the microchannel heat exchanger of mass production all has a plurality of flat pipes (heat exchanger fin), has many slight runners in it, and is equipped with the pressure manifold of mass flow and reposition of redundant personnel at the both ends of flat pipe. The collecting pipe is usually a large circular pipe, and has no flow dividing structure, fluid (refrigerant) is directly injected into the heat exchange fin, and the distribution of two-phase refrigerant in the collecting pipe is easy to be uneven.

SUMMERY OF THE UTILITY MODEL

The utility model mainly aims to provide a flow collecting structure, a micro-channel heat exchanger and an air conditioner, and aims to solve the technical problem of uneven distribution of the existing fluid.

In order to achieve the purpose, the utility model provides a flow collecting structure which comprises a base plate, wherein a plurality of channels communicated with pipelines in heat exchange plates are arranged on the base plate, each channel extends along a first direction, and the channels are distributed at intervals along a second direction;

the base plate is provided with a fluid passage communicated with the channels, the fluid passage comprises a first pore passage, a second pore passage and a third pore passage, and the first pore passage and the second pore passage are respectively arranged at two ends of the channels in the first direction and are communicated with the channels; one end of the first hole channel in the second direction is set as a first end part, and one end of the second hole channel in the second direction and far away from the first end part is set as a second end part;

the third hole channel connects the first end portion and the second end portion, and a fluid inlet and a fluid outlet are formed in the end face of the base plate.

On the basis of the technical scheme, the utility model can be further improved as follows.

Preferably, the first and second apertures are parallel and both extend in the second direction.

Preferably, an end surface of the base plate in the second direction, which is close to the second end portion, is provided as a first end surface, the third passage includes a manhole, a first flow dividing hole, and a second flow dividing hole, and one end of the manhole is provided on the first end surface;

one end of the first flow dividing hole and one end of the second flow dividing hole are connected with the manholes to form a T-shaped pipeline; the other end of the second diversion hole is connected with the second end part, and the other end of the first diversion hole is connected with the first end part through a folded hole.

Preferably, the folded duct includes a linear duct section parallel to the first duct, and a bending portion bending from one end of the linear duct section near the first end portion to the first end portion, the bending portion is connected to the first duct, and the folded duct and the first duct enclose a U shape.

Preferably, the central axes of the first duct, the second duct and the third duct are arranged on the same plane, the first flow dividing hole and the second flow dividing hole both extend along the first direction, and the zigzag duct is arranged on the side of the first duct opposite to the channel.

Preferably, the hydraulic diameters of the first cell, the second cell and the zigzag cell are the same, or the hydraulic diameters of the first cell and the zigzag cell are larger than the hydraulic diameter of the second cell.

Preferably, the hydraulic diameters of the first flow dividing hole and the second flow dividing hole are the same and are set to be D₁(ii) a The hydraulic diameters of the first pore passage, the second pore passage and the folded pore passage are set to be D₄The stroke length of the first shunt hole is set to be L₃The stroke length of the second branch orifice is set to be L₄The stroke length of the folded pore passage and the second pore passage in the second direction is set to be L₅Wherein, in the step (A),

said C is₂Is a proportionality coefficient related to the drag coefficient.

Preferably, the channel sets up to the ladder groove, the channel include by the first recess of the inside sunken formation of face of base plate, and set up the second recess of first recess tank bottom, first recess set up to with the heat exchanger fin is pegged graft, the second recess with fluid passage communicates.

Preferably, any one of the second grooves is respectively communicated with the first duct and the second duct through two connecting holes, and the ratio of the width of the connecting hole to the width of the second groove is set to be 0.8-1; the sum of the hydraulic diameters of a plurality of the connecting holes communicated with the first pore passage is set as D₅The hydraulic diameter of the first pore passage is set as D₅0.8-1 times of; the sum of the hydraulic diameters of a plurality of the connecting holes communicated with the second pore passage is set as D₆The hydraulic diameter of the second hole is set to be D₆0.8-1 times of the total amount of the active ingredients.

The utility model also provides a microchannel heat exchanger, which comprises a plurality of heat exchange sheets and two collecting structures, wherein the two collecting structures are respectively arranged at two ends of the heat exchange sheets, and the end parts of the plurality of heat exchange sheets are inserted into the channels so as to communicate the channels with pipelines in the heat exchange sheets.

The utility model also provides an air conditioner which comprises the micro-channel heat exchanger.

In the technical scheme of the utility model, aiming at the problem that the fluid can be distributed unevenly, the flow collecting structure supplies the fluid to the heat exchange fins in two opposite directions by utilizing the two branches, so that the flow distribution is realized, and the uniformity of the distribution of the refrigerant can be effectively improved through the pressure balance relationship between the two ends of the heat exchange fins.

Drawings

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

FIG. 1 is a schematic view of a manifold structure and heat exchanger plate assembly according to an embodiment of the present invention;

FIG. 2 is a schematic view of the current collection structure of FIG. 1;

FIG. 3 is an enlarged view of a portion of FIG. 2;

FIG. 4 is a schematic of a microchannel heat exchanger according to one embodiment of the utility model;

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

fig. 6 is a schematic view of the first current collection configuration of fig. 4;

FIG. 7 is a schematic cross-sectional view taken along line C-C of FIG. 6;

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

fig. 9 is a schematic view of the second current collection configuration of fig. 4;

FIG. 10 is a schematic cross-sectional view taken along line E-E of FIG. 9;

fig. 11 is a partially enlarged view of a portion F in fig. 10.

The reference numbers illustrate:

1-heat exchange plate, 2-current collecting structure, 3-base plate, 4-channel, 5-plate part, 6-tube part, 7-micro-pipeline, 8-first end face, 9-straight channel section, 10-round channel section, 11-second groove, 12-first groove, 13-second current collecting structure, 14-first current collecting structure and 15-first pore channel, 16-a second pore canal, 17-a first diversion hole, 18-a second diversion hole, 19-a manhole, 20-a folded pore canal, 21-a first end part, 22-a fourth end part, 23-a second end part, 24-a third end part, 25-a connecting hole, 26-a fifth pore canal, 27-a sixth pore canal, 28-a first connecting port and 29-a second connecting port.

The implementation, functional features and advantages of the objects of the present invention will be further explained with reference to the accompanying drawings.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

Referring to fig. 1 to 11, a flow collecting structure and a micro-channel heat exchanger according to an embodiment of the present invention are shown. The current collecting structure 2 can be used for collecting or distributing current of the heat exchanging fin 1, as shown in fig. 1 to 5, the current collecting structure 2 includes a plate-shaped base plate 3, a plurality of concave channels 4 are provided on a plate surface of one side of the base plate 3, and the channels 4 are used for being inserted and positioned with the heat exchanging fin 1. Furthermore, a fluid channel is provided in the base plate 3, which can collect the fluid in each channel 4 and lead out of the collecting structure 2, or can branch the fluid flowing into the collecting structure 2 and lead into each channel 4. From this, this mass flow structure 2 is flat to be equipped with channel 4, its bulk strength is good, can densely peg graft a plurality of heat exchanger fins 1, for the pressure manifold of present volume production has obvious promotion in the aspect of intensity, avoided the channel of intensive arrangement easily to lead to the problem of mass flow structure damage, guaranteed the intensity of heat exchanger.

First, as shown in fig. 1 to 3, any one of the channels 4 is provided as a linear groove extending in a first direction, and the plurality of channels 4 are parallel and equally spaced in a second direction, so that the channels 4 can be densely arranged. The first direction and the second direction are linear directions perpendicular to each other, but are not limited thereto, and for example, the first direction and the second direction may be curved directions. Moreover, the length of each channel 4 is equal, so that both ends of all the channels 4 in the length direction are flush, and a neat channel array is formed.

Next, in the flat plate heat exchanger 1, the plate 1 has the tubular portions 6 and the plate portions 5 alternately arranged, wherein the tubular portions 6 are in a circular tube shape, the plate portions 5 are in a flat plate shape, the tubes (microchannels 7) in the tubular portions 6 are capable of allowing the fluid to pass therethrough, and the plate portions 5 do not have the tubes. In order to match the channel 4 with the plate 1, the channel 4 comprises in its longitudinal direction (first direction) alternately arranged circular groove sections 10 and straight groove sections 9, the circular groove sections 10 being circular grooves and having dimensions corresponding to the tubular portions 6 of the plate 1 so as to correspond theretoAnd the straight groove section 9 adopts a straight line type groove, the size of the straight line type groove corresponds to the plate-shaped part 5 of the heat exchange plate 1, therefore, the heat exchange plate 1 can be accurately positioned and inserted into the channel 4, and the maximum clearance between the heat exchange plate 1 and the channel 4 after the insertion is less than 0.1. Wherein, the outer diameter of the tubular part 6 is D, the value can be between 0.3-1.2mm, the wall thickness of the tubular part 6 is between 0.1-0.4mm, and the corresponding circular groove section 10 is matched with the size thereof; the thickness of the plate-shaped part 5 is H, the value of H is between 0.1 and 0.6mm, and the groove width dimension of the straight groove section 9 is also matched with H. In addition, the distance L between two adjacent heat exchange plates 1 (i.e. the distance between two channels 4)₁The distance is between 1.0 mm and 2.2mm, all the distances are not required to be equal, and the product differentiation design can be carried out according to specific requirements; the width (i.e. the length of the channel 4 in the first direction) L of the plate 1₂Can be 8-35 mm.

In addition, the channel 4 is a stepped channel, that is, the circular channel section 10 and the straight channel section 9 are stepped channels, and the channel 4 includes a first groove 12 formed by recessing a side plate surface of the substrate 3 towards the inner side of the plate and a second groove 11 formed by recessing the bottom of the first groove 12 further inwards in the depth direction of the channel, the width of the second groove 11 is smaller than that of the first groove 12, and the size of the first groove 12 is matched with that of the heat exchange plate 1 to form a stepped channel. When the heat exchange plate 1 is inserted into the channel 4, the width of the second groove 11 is smaller, the heat exchange plate 1 is only inserted into the first groove 12, the end part of the heat exchange plate abuts against the bottom of the first groove 12, the bottom of the first groove 12 limits the heat exchange plate 1, and the second groove 11 can allow fluid to flow along the first direction. Therefore, the heat exchange sheet 1 is limited, and meanwhile, the fluid permeability of the channel 4 in the length direction is ensured. The groove depth of the groove 4 is one third of the thickness of the substrate, but is not limited thereto, for example, the groove depth may also be one half, one quarter, etc. of the thickness of the substrate 3, and is not more than one half of the thickness of the substrate 3, which is beneficial to ensuring the overall strength of the current collecting structure.

In some exemplary embodiments, the base plate 3 is a single piece that can be formed by printing, injection molding, etc., and it can also be of a detachable construction, i.e., the base plate 3 includes a detachably attachable cover plate and a base plate, the cover plate can be attached to the base plate by fasteners, etc., and the channels 4 are disposed on the cover plate, and the fluid passages are partially disposed on the cover plate and partially disposed on the base plate, thereby reducing the difficulty of machining the base plate 4.

As shown in fig. 4, both ends of each heat exchanging fin 1 are connected to the flow collecting structure 2, so that a microchannel heat exchanger can be formed, the end of each heat exchanging fin 1 is inserted into the channel 4 on the substrate 3, and the second groove 11 of the channel 4 is communicated with the pipeline (micro pipeline 7) in the heat exchanging fin 1, so that the construction of a fluid pipeline of the microchannel heat exchanger is completed, fluid can enter the microchannel heat exchanger from one flow collecting structure 2 and then flow to each heat exchanging fin 1, and the fluid flowing through the heat exchanging fins 1 can be collected and flow out in the other flow collecting structure. In addition, the heat exchanger plate 1 needs to be further fixed with the base plate 3 besides being inserted into the groove 4, and the two can be fastened by welding, but not limited to this, for example, clamping or connecting the two by fasteners, the plate-shaped base plate 3 provides more connecting ways than the existing collecting pipe, and is not limited to welding.

The two collecting structures 2 at the two ends of the heat exchange plate can adopt two collecting structures with the same fluid channel or two collecting structures with different fluid channels. As also shown in fig. 4, the two current collecting structures 2 may be divided into a second current collecting structure 13 and a first current collecting structure 14 due to different installation locations, the second current collecting structure 13 and the first current collecting structure 14 have different fluid passages, the first current collecting structure 14 may be used for distributing current in the evaporation condition, and the second current collecting structure 13 may be used for collecting current in the evaporation condition. Aiming at the flow dividing process, at present, the existing collecting pipe channel directly supplies fluid to each heat exchange plate 1 without flow dividing, and the distribution of two-phase refrigerants in the collecting pipe is easy to be uneven, so that the performance attenuation problem exists. Aiming at the flow collecting process, the inlet of the existing flow collecting pipe channel is a two-phase refrigerant, the flow speed is low, the outlet is a gaseous refrigerant, the flow speed is high, the pressure difference along the outlet is gradually increased, so that the flow passing through the heat exchange plate 1 is also gradually increased, and the uneven flow distribution and the performance attenuation of the heat exchanger are caused.

The two collecting structures 2 with different positions have the same characteristics with respect to the base plate 3 and the channel 4, except for different flow paths. In some exemplary embodiments, as shown in fig. 6-8, the manifold structure may be used for splitting, i.e. dividing the fluid into a plurality of sub-streams into heat exchanger plates 1, and is formed by a base plate 3, the plate surface of the base plate 3 having the above-mentioned channels 4, and a plurality of regularly arranged channels 4 forming an array. The flow path of the manifold structure, which is primarily formed by the third and second channels 16, and the first channel 15, distributes the coolant into each channel 4. In particular, the first duct 15 is located on one side of the channel array and the second duct 16 is located on the other side of the channel array, i.e. the first duct 15 and the second duct 16 are located at both ends of the channel 4 in the first direction, so that both ends of the channel 4 are close to the first duct 15 and the second duct 16, respectively, and the second recess 11 of the channel 4 communicates with both. As the channels 4 are all equally long and flush, the first porthole 15 and the second porthole 16 extend in the second direction.

As shown in fig. 7, the first duct 15 has two ends, namely a first end 21 remote from the first end surface 8 and a third end 24 close to the first end surface 8. The second porthole 16 also has two ends, which are located at two ends in the second direction, specifically a second end 23 and a fourth end 22, the second end 23 being located at a side close to the first end surface 8 and being relatively distant from the first end 21. So that the first end portion 21 and the second end portion 23 are located at opposite corners of the substrate 3. One end of the second groove 11 of the channel 4 in the length direction is respectively communicated with the first pore passage 15 through a connecting hole 25, and the other end is communicated with the second pore passage 16 through the connecting hole 25, so that the channel 4 is communicated with the fluid passage.

As shown in fig. 8, the width of the connection hole 25 refers to the distance between the two hole walls in the second direction, and can be represented as f, and the relationship between f and the groove width of the second groove 11 is that the value of f is between 0.8 times and 1 times of the groove width, and in this example, f is equal to 0.9 times of the groove width. Specifically, all the connection holes 25 on the substrate may be classified into two types, i.e., a first through hole and a second through hole, according to the position and the object of the connection. The first through hole and the second through hole are respectively arranged at two ends of the channel, and the positions of the first through hole and the second through hole are different. The first through-hole connects the channel 4 to the first duct 15, and the second through-hole connects the channel 4 to the second duct 15The second duct 16 is connected to a different object. The first and second through holes are equal in number and have the same respective stroke length and total hydraulic diameter. The sum of the hydraulic diameters of all the first through holes is equal to the sum of the hydraulic diameters of all the second through holes, and is represented by D₅＝D₆. The hydraulic diameter of the first port 15 and the hydraulic diameter of the second port 16 may both be set to D₅0.8 to 1 times, and a relationship of 0.9 times is obtained in this example. If the hydraulic diameter of the first port 15 and the hydraulic diameter of the second port 16 are different, D₅And D₆And different as long as the hydraulic diameter of the first porthole 15 is ensured to be D₅0.8 to 1 times, the second porthole 16 has a hydraulic diameter D₆0.8 to 1 time of the total amount of the above-mentioned components, respectively.

One end of the third pore canal is positioned on the side wall of the substrate 3 and is used as a fluid inlet and outlet, the other end of the third pore canal forms a two-way branch which is connected with the first end part 21 and the second end part 23, so that the first pore canal 15 and the second pore canal 16 are communicated, and the first flow collecting structure 14 is formed by a flow collecting structure with the fluid channel. Specifically, one sidewall of the substrate 3 is a first end surface 8, and the first end surface 8 is perpendicular to the second direction and is close to the second end portion 23.

The third flow channel comprises not only a manhole 19 for outgoing liquid but also a second porthole 18 and a first porthole 17 for splitting the flow, wherein one end of the manhole 19 leads to the first end surface 8, so that the flow can be injected from the manhole 19 into the third flow channel. All three being rectilinear, the first tapping orifice 17 is connected at one end to the end of the manhole 19, which is also connected to one end of the second tapping orifice 18. At the same time, the first porthole 17 extends in a first direction, the second porthole 18 also extends in a first direction, and the manhole 19 is perpendicular to the first direction, which form a "T" shaped conduit. At the same time, the other end of the first flow-dividing opening 17 is connected to the first end 21 via the bellows 20, while the other end of the second flow-dividing opening 19 is connected to the second end 23.

As shown in fig. 7, the folded duct 20 is composed of a straight section and a bent section, which are connected to each other, and the straight section is parallel to the first duct 15, i.e., extends along the second direction. The bent portion is located at an end of the linear bore section away from the first branch bore 17, and the bent portion may extend in the first direction so as to be bent toward the first end portion 21 and connected to the first bore 15. This makes the whole of the zigzag duct 20 in an L-shape, and the zigzag duct 20 and the straight first duct 15 enclose a U-shaped flow channel. In addition, for convenience of processing, the central axes of the third duct, the second duct 16 and the first duct 15 are all located on the same plane, and the folded duct 20 is located on the side of the first duct 15 facing away from the second groove 11.

Therefore, the fluid channel forms two branches for fluid to flow to the heat exchange plate 1, one branch is a first fluid channel, the other branch is a second fluid channel, the first fluid channel consists of a first branch hole 17, a folded hole channel 20 and a first hole channel 15, the second fluid channel consists of a second hole channel 16 and a second branch hole 17, the tail end of the first fluid channel is a third end portion 23, and the tail end of the second fluid channel is a fourth end portion 22, so that the flow is further divided. When fluid enters the inlet port 19, it may be split, some fluid flows through the first fluid passage, and another part flows through the second fluid passage, and the fluid in the first fluid passage will first reach the first end 21 through the folded passage 20, and finally reach the third end 24, and then flow into the corresponding plate 1 from the left side to the right side in the second direction. Fluid from the second fluid path will first reach the right second end 23 and only then reach the left fourth end 22, resulting in a second direction from right to left into the corresponding plate 1. Whereas for a single plate 1, for example the rightmost plate 1 in the second direction, one end is adjacent the second end 23 and thus contacts the fluid (refrigerant) first, and the other end is adjacent the third end 24 and is downstream of the first fluid path and contacts the fluid relatively later, and the rightmost plate 1 in the second direction is the opposite. Therefore, the flow collecting structure supplies fluid to the heat exchange fins in two opposite directions by utilizing the two branches to realize flow distribution, and the uniformity of refrigerant distribution can be effectively improved through the pressure balance relationship at the two ends of the heat exchange fins.

As shown in fig. 8, the zigzag channels 20 have a hydraulic diameter corresponding to that of the first channels 15. At the same time, the second port channel 16 is also designed with the same hydraulic diameter. The hydraulic diameter of the three can be expressed as D₄D of the above₄Has a value between D₅Between 0.8 and 1 times. The D₄Can also be represented as₆Is the relationship of (1) or (D)₆0.8 to 1 times of. The design of uniform hydraulic diameter can facilitate processing and manufacturing, and save manufacturing cost.

Without being limited thereto, it is also possible to design the first porthole 15 and the accordion porthole 20 to have the same hydraulic diameter, but different from the second porthole 16, the hydraulic diameters of the first and second portholes being larger than the hydraulic diameter of the second porthole 16, which makes it possible to compensate for the pressure loss over a longer stroke. The hydraulic diameter of the first porthole 17 is also identical to the hydraulic diameter of the second porthole 18, both indicated by D₁. The first tapping hole 17 extends in a first direction so that its stroke length, in particular L, is available₃. The second flow-dividing opening 18 also extends in the first direction, so that the passage length of this duct, in particular L, is obtained₄. The two ends of the zigzag duct 20 in the second direction are flush with the two ends of the second duct 16 in the second direction, so that the stroke lengths of the two ducts in the second direction are the same and are both L₅. To this end, the dimensions of the flow passages need to be ensured to comply with the relationship

Wherein, C₂Expressed as a proportionality coefficient related to the drag coefficient.

In some exemplary embodiments, as shown in fig. 9 to 11, the current collecting structure also has the substrate 3, and the substrate 3 has the aligned channels 4 on one side of the substrate. The flow channels of the manifold structure are likewise formed by the third cell channels, the second cell channels 16 and the first cell channels 15. In particular, a first aperture 15 is located on one side of the array of channels and a second aperture 16 is located on the other side of the array of channels, which may also be stated as being at both ends of the channels 4 in the first direction. And the channel 4 is in turn connected at both ends to a first port channel 15 and a second port channel 16, respectively. In addition, since the channel 4 is equal in length and flush, the first duct 15 and the second duct 16 both extend along the second direction, and both ends of the second groove 11 of the channel 4 in the length direction are respectively communicated with the first duct 15 and the second duct 16 through the connecting hole 25. In particular, the first duct 15 presents a first connection port 28 along its length, the second duct 15 presents a second connection port 29 along its length, one end of the third duct is located on the side wall of the base plate 3, forming an outlet for the fluid, and the third duct is also in communication with the first connection port 28 and the second connection port 29, constituting the above-mentioned second collecting structure 13.

As shown in fig. 11, the width of the connection hole 25 refers to the distance between two hole walls in the second direction, and may be represented as f, where f is between 0.8 times and 1 times the width of the second groove 11, and in this example, f is equal to 0.9 times the width of the second groove. All the connection holes 25 on the substrate may be classified into two types, i.e., a first through hole and a second through hole, according to the position and the object of the connection. The first through hole and the second through hole are respectively arranged at two ends of the channel, and the positions of the first through hole and the second through hole are different; the first through hole connects the channel 4 to the first hole 15, and the second through hole connects the channel 4 to the second hole 16, which are different from each other. The first and second through holes are equal in number and have the same respective stroke length and total hydraulic diameter. The sum of the hydraulic diameters of all the first through holes is equal to the sum of the hydraulic diameters of all the second through holes, and is represented by D₅＝D₆. The hydraulic diameter of the first port 15 and the hydraulic diameter of the second port 16 may both be set to D₅0.8 to 1 times, and a relationship of 0.9 times is achieved in the present example. If the hydraulic diameter of the first port 15 and the hydraulic diameter of the second port 16 are different, D₅And D₆And different as long as the hydraulic diameter of the first porthole 15 is ensured to be D₅0.8 to 1 times, the second porthole 16 has a hydraulic diameter D₆0.8 to 1 time of the total amount of the above-mentioned components, respectively.

One side wall of the base plate 3 is a first end surface 8, and the third channel includes not only a liquid outlet manhole 19, but also a second flow dividing hole 18 and a first flow dividing hole 17 for dividing the fluid, wherein one end of the manhole 19 leads to the first end surface 8, so that the fluid can flow out of the third channel through the manhole 19. All three being rectilinear, the first tap hole 17 being connected at one end to the end of the manhole 19, which end is also connected to one end of the second tap hole 18, said first tap hole 17 and said second tap hole 18 both extending in a first direction, the manhole 19 being perpendicular to the first direction, the three forming a "T" shaped duct.

In contrast to the first collecting configuration, the second flow dividing opening 18 no longer connects to the end of the second port channel 16, but rather to the second connection opening 29 via the sixth port channel 27, and the first flow dividing opening 17 is also not connected to the end of the first port channel 15, but rather to the first connection opening 28 via the fifth port channel 26. The second connection port 29 and the first connection port 28 may be centrally located on the second bore 16 and the first bore 15, respectively, or may be located elsewhere, in this example, the second connection port 29 and the first connection port 28 are both approximately centrally located. The fifth port channel 28 extends from the first branch hole 17 in the second direction, and the end of the fifth port channel 28 away from the first branch hole 17 extends to the corresponding position of the first connection port 28, turns to the side of the first connection port 28, and extends until being connected to the first port channel 15; the sixth port channel 27 extends from the second branch flow hole 18 in the second direction, and the end of the sixth port channel 27, which is far from the second branch flow hole 18, extends to the corresponding position of the second connection port 29, and is not extended further in the second direction, but is turned to the side of the second connection port 29 until being connected to the second port channel 16. Meanwhile, the central axes of the third hole channel and the second hole channel 16, as well as the central axis of the first hole channel 15 are all in the same plane, which is convenient for processing, the position of the fifth hole channel 26 in the base plate 3 is at the side of the first hole channel 15 facing away from the second groove 11, and the position of the sixth hole channel 27 in the base plate 3 is at the side of the second hole channel 16 facing away from the second groove 11.

The fluid passages shown in figures 9 to 11 thus also form two branches for fluid to flow to plate 1, one being a third fluid passage and the other being a fourth fluid passage, the third fluid passage being formed by the first flow-dividing aperture 17, the fifth port passage 26 and the first port passage 15 in series. The fourth fluid passage is formed by the second flow-dividing aperture 18, the sixth port 27 and the second port 16 which are connected in series, and the manhole 19 is arranged centrally of the channel so that the stroke length of the third fluid passage is substantially the same as the stroke length of the fourth fluid passage, in mirror image relationship. The fluid in the heat exchanger plate 1 can flow to both ends in the length direction after entering the second groove 11, and is divided into two branches to flow into the first duct 15 and the second duct 16, and the two branches flow into the third duct by being respectively concentrated in the center of the first duct 15 and the center of the second duct 16. It can be seen that of the plurality of plates 1, the plate 1 centered in the second direction has the shortest fluid flow path and relatively less pressure loss. Therefore, the second flow collecting structure adopts the fluid channel which is collected and discharged in the middle, and the flow can be reduced, so that the pressure loss is reduced, and the function of balancing the flow is achieved. In combination with the first flow concentration structure, fluid preferentially flows into the heat exchange plates 1 from two ends in the second direction, the heat exchange plate 1 in the middle in the second direction is relatively contacted with the fluid 1 later, pressure loss is slightly high, the second flow concentration structure utilizes the liquid discharged from the middle in the second direction, the pressure loss of the fluid flowing through the heat exchange plates 1 is reduced, the distribution uniformity of the refrigerant in the heat exchanger is further improved, and the heat exchange performance is improved.

In addition, when the second flow collecting structure is installed, the first hole channels 15 may be needed to correspond to the windward side of the heat exchange plate 1, and the second hole channels 16 are located on the leeward side, in this case, the hydraulic diameter of the first hole channels 15 can be preferentially designed to be larger than that of the second hole channels 16. The design is high in heat exchange efficiency on the windward side, the total flow of the refrigerant is large, the flow speed is large, the circulation aperture is properly increased, the pressure loss can be reduced, and the effect of balancing the flow can be realized.

In the present example, the hydraulic diameter of the first porthole 17 is identical to the hydraulic diameter of the second porthole 18, both denoted D₁. The hydraulic diameters of the fifth port channel 26 and the sixth port channel 27 are kept the same, both denoted D₂. The hydraulic diameter of the first port 15 is equal to the hydraulic diameter of the second port 16, but both are smaller than the sixth port 27 and the fifth port 26, the first port 15 and the second port 1Hydraulic diameter of 6 is denoted D₄. The first tapping hole 17 extends in a first direction so that its stroke length, in particular L, is available₃. The second flow-dividing opening 18 also extends in the first direction, so that the passage length of this duct, in particular L, is obtained₄. As further shown in fig. 10, a portion of the fifth port channel 26 extends in the second direction, such that a stroke length of the portion, specifically L, is obtained₆. A part of the cells of the sixth cell 27 also extends in the second direction, and the stroke length of this part, in particular L, is obtained₇. To this end, the above-mentioned flow passage dimension of the fluid passage needs to ensure that the following relationship holds

The C is₁Is a proportionality coefficient related to the drag coefficient, and D₂1.6 to 2 times of D₄。

In other exemplary embodiments, the microchannel heat exchanger may include two first current collecting structures, or two second current collecting structures.

In an exemplary embodiment, an air conditioner includes the above-described microchannel heat exchanger.

In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the utility model and to simplify the description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting of the utility model.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless explicitly specified otherwise.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meanings of the above terms in the present invention can be understood according to specific situations by those of ordinary skill in the art.

In the present invention, unless expressly stated or limited otherwise, the first feature "on" or "under" the second feature may be directly contacting the second feature or the first and second features may be indirectly contacting each other through intervening media. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

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

Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.

Claims

1. A flow collecting structure is characterized by comprising a base plate, wherein a plurality of channels communicated with pipelines in heat exchange plates are arranged on the base plate, each channel extends along a first direction, and the channels are distributed at intervals along a second direction;

2. The current collecting structure of claim 1, wherein the first and second cell channels are parallel and each extend in the second direction.

3. The current collecting structure of claim 2, wherein an end surface of the substrate in the second direction adjacent to the second end portion is provided as a first end surface, the third aperture includes a manhole, a first flow dividing hole, and a second flow dividing hole, one end of the manhole being provided on the first end surface;

4. The current collecting structure according to claim 3, wherein the folded duct includes a straight section parallel to the first duct, and a bent section bent from an end of the straight section near the first end toward the first end, the bent section is connected to the first duct, and the folded duct and the first duct form a U-shape.

5. The current collecting structure according to claim 3, wherein central axes of the first, second and third cell channels are disposed on the same plane, the first and second flow dividing holes each extend in the first direction, and the zigzag-shaped cell channels are disposed on a side of the first cell channel facing away from the channel.

6. The current collecting structure of claim 3, wherein the hydraulic diameters of the first cell channels, the second cell channels and the corrugated cell channels are the same or the hydraulic diameters of the first cell channels and the corrugated cell channels are greater than the hydraulic diameter of the second cell channels.

7. The flow collection structure of claim 6, wherein the first and second flow distribution holes have the same hydraulic diameter and are both set at D₁(ii) a The hydraulic diameters of the first pore passage, the second pore passage and the folded pore passage are set to be D₄The stroke length of the first shunt hole is set to be L₃The stroke length of the second branch orifice is set to be L₄The stroke length of the folded pore passage and the second pore passage in the second direction is set to be L₅Wherein, in the step (A),

said C is₂Is a proportionality coefficient related to the drag coefficient.

8. The current collecting structure as claimed in any one of claims 1 to 7, wherein the channel is configured as a stepped slot, the channel including a first groove formed by an inward depression of the face of the substrate, and a second groove disposed at the bottom of the first groove, the first groove configured to engage the heat exchanger fins, the second groove communicating with the fluid passage.

9. The current collecting structure according to claim 8, wherein any one of the second grooves communicates with the first cell channels and the second cell channels through two connecting holes, respectively, and the ratio of the width of the connecting hole to the width of the second groove is set to 0.8-1; the sum of the hydraulic diameters of a plurality of the connecting holes communicated with the first pore passage is set as D₅The hydraulic diameter of the first pore passage is set as D₅0.8-1 times of; the sum of the hydraulic diameters of a plurality of the connecting holes communicated with the second pore passage is set as D₆The hydraulic diameter of the second hole is set to be D₆0.8-1 times of the total amount of the active ingredients.

10. A microchannel heat exchanger comprising a plurality of plates, and two manifold structures according to any one of claims 1-9, wherein the two manifold structures are disposed at opposite ends of the plates, and wherein the ends of the plurality of plates are inserted into the channels to communicate the channels with the tubes in the plates.

11. An air conditioner comprising the microchannel heat exchanger of claim 10.