CN113267077A

CN113267077A - But mass flow structure, microchannel heat exchanger and air conditioner

Info

Publication number: CN113267077A
Application number: CN202110719778.8A
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: 2021-08-17

Abstract

The invention discloses a flow collecting structure, a micro-channel heat exchanger and an air conditioner, wherein the flow collecting structure comprises a substrate, wherein a plurality of channels are arranged on the surface of one side of the substrate and used for being inserted and positioned with heat exchange fins; and a fluid passage is arranged in the base plate, is communicated with the plurality of channels and is used for collecting the fluid in the plurality of channels and leading out of the collecting structure or shunting and leading the fluid flowing into the collecting structure into the plurality of channels. The microchannel heat exchanger 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 heat exchange sheets are inserted into the channels so as to communicate the channels with pipelines in the heat exchange sheets. The air conditioner includes a microchannel heat exchanger. The technical scheme provided by the invention aims to solve the technical problem that the current densely arranged channels are easy to cause damage to the current collecting structure.

Description

But mass flow structure, microchannel heat exchanger and air conditioner

Technical Field

The invention 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. This pressure manifold is big pipe usually, and the pipe side is seted up the channel, supplies flat pipe (heat exchanger fin) to insert, and the tip disect insertion of flat pipe is to the pressure manifold, when flat pipe interval is showing and is reducing, need set up intensive channel on the pressure manifold, because pipe wall itself is thinner, the processing degree of difficulty grow also leads to the pressure manifold to damage easily.

Disclosure of Invention

The invention mainly aims to provide a current collecting structure and a micro-channel heat exchanger, and aims to solve the technical problem that the current densely distributed channels are easy to cause damage to the current collecting structure.

In order to achieve the purpose, the flow collecting structure provided by the invention comprises a substrate, wherein a plurality of channels are arranged on the surface of one side of the substrate and are used for being inserted and positioned with heat exchange sheets; and a fluid passage is arranged in the base plate, is communicated with the plurality of channels and is used for collecting the fluid in the plurality of channels and leading out of the collecting structure or shunting and leading the fluid flowing into the collecting structure into the plurality of channels.

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

Preferably, the channel sets up to the ladder groove that extends along first direction, the channel include by the face of base plate is the first recess of the inside sunken formation, and set up the second recess of first recess tank bottom, the tank bottom of first recess sets up to spacing the heat exchanger fin.

The beneficial effect who adopts above-mentioned further scheme is, when spacing to the heat transfer piece, guarantees the fluid trafficability characteristic of channel in its length direction.

Preferably, a plurality of the channels are arranged in parallel and distributed at intervals along the second direction, and two ends of each channel in the first direction are flush to form a channel array.

Preferably, the channel includes round groove section and straight groove section that set up in turn in first direction, the round groove section set up to round groove and with the cast portion of heat exchanger fin corresponds, the straight groove section set up to straight line type groove and with the platelike portion of heat exchanger fin corresponds.

Preferably, the fluid passage includes a first hole passage and a second hole passage, the first hole passage and the second hole passage extend along the second direction and are respectively located at two ends of the channel in the first direction, and the first hole passage and the second hole passage are both communicated with the second groove.

Preferably, the fluid passage includes a third bore, the third bore communicating the first and second bores.

Preferably, the base plate is provided as a single piece; or the base plate comprises a cover plate and a bottom plate which are detachably connected, the cover plate covers the bottom plate, and the channel is arranged on the cover plate.

Adopt the beneficial effect of above-mentioned further scheme to be, guarantee the bulk strength of mass flow structure.

The invention 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, the end parts of the heat exchange sheets are inserted into the channels, and the channels are communicated with the pipelines in the heat exchange sheets.

Preferably, the heat exchange plate is welded, clamped or connected with the base plate through a fastener

The beneficial effect who adopts above-mentioned further scheme is that, channel and heat exchanger fin can further be fixed, guarantee stability, can realize multiple connected form moreover, and not only be limited to the welding.

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

In the technical scheme of the invention, aiming at the problem that the current collecting structure is easy to damage due to the intensive installation of the heat exchange plates, the current collecting structure realizes the stable mechanical property between the channels by means of the support of the substrate material, and ensures the reliability of the product.

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 invention;

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 platelike 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 circularThe size of the straight groove section 9 is corresponding to the plate-shaped part 5 of the heat exchange plate 1, so that the straight groove section can be conveniently inserted, the size of the straight groove section is corresponding to the pipe-shaped part 6 of the heat exchange plate 1, therefore, the heat exchange plate 1 can be accurately positioned and inserted into the groove channel 4, and the maximum gap between the heat exchange plate 1 and the groove channel 4 after 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 adopts a stepped groove, that is, the circular groove section 10 and the straight groove section 9 are stepped grooves, and the channel 4 comprises a first groove 12 formed by inwards recessing the plate surface of the substrate 3 and a second groove 11 positioned at the bottom of the first groove 12 in the depth direction of the channel, wherein 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 groove. 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 a first end 21 and a third end 24 at two ends, and the first end 21 is far from the first end face 8; the second cell 16 has a second end 23 and a fourth end 22 at two ends in the second direction, the second end 23 is close to the third end 24 and is relatively far from the first end 21, and the first end 21 and the second end 23 correspond to two opposite corners of the substrate 3. Both ends of the second groove 11 of the channel 4 in the length direction are respectively communicated with the first pore passage 15 and the second pore passage 16 through the connecting hole 25. The width (i.e. the dimension in the second direction) of the connection hole 25 is f, which has a value between 0.8 and 1 times the groove width of the second recess 11. The number of the connecting holes 25 connecting the first port 15 and the number of the connecting holes 25 connecting the second port 16 are the same, and the stroke length and the hydraulic diameter are the same, that is, the sum of the hydraulic diameters of all the connecting holes 25 communicating with the first port 15 is equal to the sum of the hydraulic diameters of all the connecting holes 25 communicating with the second port 16, and is denoted by D₅＝D₆The hydraulic diameters of the first and

second ports

15 and 16 are set to D₅0.8-1 times of the total amount of the active ingredients. If the hydraulic diameters of the first port 15 and the second port 16 are different, D₅And D₆And different as long as the hydraulic diameter of the first porthole 15 is ensured to be D₅0.8-1 times of the water of the second pore passage 16Force diameter of D₆0.8-1 times of the total amount of the active ingredients.

One end of the third pore channel 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 channel forms a two-way branch which is connected with the first end part 21 and the second end part 23 so as to be communicated with the first pore channel 15 and the second pore channel 16, and the first current collecting structure 14 is formed by a current 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 channel can be subdivided into a first flow dividing hole 17, a second flow dividing hole 18 and a manhole 19 according to the trend, wherein the three holes are linear holes, one end of the manhole 19 is positioned on the first end surface 8, and fluid can enter the third channel from the manhole 19 to realize fluid injection. The first flow-dividing aperture 17 is connected at one end to the end of a manhole 19 which is also connected to one end of a second flow-dividing aperture 18, the first and second flow-dividing

apertures

17 and 18 both extending in a first direction, the manhole 19 being perpendicular to the first direction, the three forming 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 parallel to the first duct 15, i.e. extending along the second direction, and a bent section located at an end of the straight section away from the first branch flow hole 17, the bent section extending along the first direction to form a bend toward the first end 21 and being connected to the first duct 15, so that the folded duct 20 is L-shaped as a whole, and the folded duct 20 and the straight first duct 15 enclose a U-shaped flow channel. In addition, for the convenience of processing, the central axes of the third duct and the first and

second ducts

15, 16 are all on the same plane, and the folded duct 20 is located on the side of the first duct 15 opposite to the channel 4.

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 can 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.

In addition, the hydraulic diameter of the zigzag type pore canal 20 is consistent with that of the second pore canal 16, and the same hydraulic diameter is also adopted for the first pore canal 15, and the hydraulic diameters are all D₄D of the above₄Has a value between D₅0.8 to 1 times of (A), and can also be expressed as D₆0.8-1 times of the total diameter of the first duct 15 and the folded duct 20, thereby saving the manufacturing cost, but not limited to this, the hydraulic diameter of the first duct 15 and the folded duct 20 can be designed to be the same, but different from the second duct 16, the hydraulic diameter of the second duct 16 is smaller than the hydraulic diameter of the first duct and the folded duct, and the design can compensate the pressure loss with longer stroke. The first and second

flow dividing openings

17, 18 have the same hydraulic diameter, which is D₁The stroke length (i.e., the length in the first direction) of the first branch orifice 17 is L₃Row of second tapping holes 18The path length (i.e. the length in the first direction) is L₄. The two ends of the above-mentioned folded duct 20 in the second direction are identical to the two ends of the second duct 16 in the second direction, so that the stroke lengths of the two in the second direction are identical and are both L₅Wherein the flow passages are required to satisfy the following relationship

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

In some exemplary embodiments, as shown in fig. 9 to 11, the current collecting structure is composed of the substrate 3, and the substrate 3 has a side plate surface provided with regularly arranged channels 4. The fluid channels of the manifold structure are primarily formed by the second and

first cell channels

16, 15, and the third cell channels. Wherein the first porthole 15 is located at one side of the channel array and the second porthole 16 is located at the other side of the channel array, i.e. at both ends of the channel 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. The width (i.e. the dimension in the second direction) of the connection hole 25 is f, which has a value between 0.8 and 1 times the groove width of the second recess 11. The number of the connecting holes 25 connecting the first port 15 and the number of the connecting holes 25 connecting the second port 16 are the same, and the stroke length and the hydraulic diameter are the same, that is, the sum of the hydraulic diameters of all the connecting holes 25 communicating with the first port 15 is equal to the sum of the hydraulic diameters of all the connecting holes 25 communicating with the second port 16, and is denoted by D₅＝D₆The hydraulic diameters of the first and

second ports

15 and 16 are set to D₅0.8-1 times of the total amount of the active ingredients. If the hydraulic diameters of the first port 15 and the second port 16 are different, D₅And D₆And different as long as the hydraulic diameter of the first porthole 15 is ensured to be D₅0.8-1 times, the hydraulic diameter of the second porthole 16 is D₆0.8-1 times of the total amount of the active ingredients. In particular, the first duct 15 is oriented in the direction of its lengthThe first connection port 28 is present, while the second port channel 15 has a second connection port 29 along its length, one end of the third port channel being located on the side wall of the base plate 3 and forming an outlet for the fluid, the third port channel further communicating with the first connection port 28 and the second connection port 29 to form the second current collecting structure 13.

One side wall of the substrate 3 is a first end surface 8, and the third channel is mainly composed of a first flow dividing hole 17, a manhole 19 and a second flow dividing hole 18, wherein one end of the manhole 19 is located on the first end surface 8, and fluid can flow out of the third channel through the manhole 19. The third channel can be subdivided into a first flow dividing hole 17, a second flow dividing hole 18 and a manhole 19 according to the trend, wherein the three holes are linear holes, one end of the manhole 19 is positioned on the first end surface 8, and fluid can enter the third channel from the manhole 19 to realize fluid injection. The first flow-dividing aperture 17 is connected at one end to the end of a manhole 19 which is also connected to one end of a second flow-dividing aperture 18, the first and second flow-dividing

apertures

17 and 18 both extending in a first direction, the manhole 19 being perpendicular to the first direction, the three forming a "T" shaped conduit.

In contrast to the first collecting structure, the other end of the second flow dividing opening 18 is no longer connected to the end of the second port 16, but is connected to the second connection opening 29 via the sixth port 27, and the other end of the first flow dividing opening 17 is not connected to the end of the first port 15, but is connected to the first connection opening 28 via the fifth port 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.

Thus, the fluid passageways shown in figures 9 to 11 also form two branches for fluid to flow towards the plate 1, one being a third fluid passageway formed by the first porthole 17, the fifth porthole 26 and the first porthole 15 which are connected in series, the other being a fourth fluid passageway formed by the second porthole 18, the sixth porthole 27 and the second porthole 16 which are connected in series, the porthole 19 being centrally located relative to the channel such that the stroke length of the third fluid passageway is the same as that of the fourth fluid passageway, 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, the first channel 15 of the second flow collection structure may be located on the windward side of the plate 1, and the second channel 16 may be located on the leeward side of the plate 1, and the hydraulic diameter of the first channel 15 may be designed to be larger than that of the second channel 16. The design is due to the windward sideThe heat exchange efficiency is high, the total flow of the refrigerant is large, the flow velocity 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 diameters of the first and second

flow dividing openings

17, 18 are both set to D₁The hydraulic diameters of the fifth port passage 26 and the sixth port passage 27 are set to D₂The hydraulic diameters of the first port 15 and the second port 16 are set to D₄The stroke length of the first branch orifice 17 in the first direction is L₃The stroke length of the second branch orifice 18 in the first direction is L₄The stroke length of the fifth port passage 26 in the second direction is L₆The stroke length of the sixth orifice 27 in the second direction is set to L₇Wherein it is necessary to ensure that the 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 invention 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 invention.

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 specifically limited 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 by those skilled in the art according to specific situations.

In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. 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 invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

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 are arranged on the surface of one side of the base plate and used for being inserted and positioned with heat exchange sheets; and a fluid passage is arranged in the base plate, is communicated with the plurality of channels and is used for collecting the fluid in the plurality of channels and leading out of the collecting structure or shunting and leading the fluid flowing into the collecting structure into the plurality of channels.

2. The current collecting structure of claim 1, wherein the channel is configured as a stepped slot extending in a first direction, the channel including a first groove formed by an inward depression of the plate surface of the base plate and a second groove disposed at a bottom of the first groove, the bottom of the first groove configured to retain the heat exchanger fins.

3. The current collecting structure of claim 2, wherein a plurality of said channels are arranged in parallel and spaced apart in the second direction, each of said channels being aligned at both ends in the first direction to form an array of channels.

4. The flow collection structure of claim 2, wherein the channels comprise alternating in the first direction circular channel segments and straight channel segments, the circular channel segments being arranged as circular channels and corresponding to the tube-shaped portions of the fins, and the straight channel segments being arranged as straight channel segments and corresponding to the plate-shaped portions of the fins.

5. The current collecting structure of claim 3, wherein the fluid passage includes first and second channels extending in the second direction and located at opposite ends of the channel in the first direction, the first and second channels each communicating with the second recess.

6. The current collecting structure of claim 5, wherein the fluid passage includes a third channel, the third channel communicating the first and second channels.

7. The current collecting structure of any of claims 1-6, wherein the substrate is provided as a unitary piece; or the base plate comprises a cover plate and a bottom plate which are detachably connected, the cover plate covers the bottom plate, and the channel is arranged on the cover plate.

8. A microchannel heat exchanger comprising a plurality of plates, and two manifold structures according to any one of claims 1-7, wherein the two manifold structures are disposed at opposite ends of the plates, and wherein the ends of the plates are inserted into the channels, and wherein the channels communicate with the tubes in the plates.

9. The microchannel heat exchanger of claim 8, wherein the plate is welded, snapped, or otherwise attached to the base plate with fasteners.

10. An air conditioner comprising the microchannel heat exchanger of claim 8 or 9.