CN214199287U

CN214199287U - Heat exchanger and air conditioner

Info

Publication number: CN214199287U
Application number: CN202023075767.0U
Authority: CN
Inventors: 何哲旺
Original assignee: GD Midea Air Conditioning Equipment Co Ltd
Current assignee: GD Midea Air Conditioning Equipment Co Ltd
Priority date: 2020-12-18
Filing date: 2020-12-18
Publication date: 2021-09-14
Anticipated expiration: 2030-12-18

Abstract

The utility model discloses a heat exchanger and air conditioner. The heat exchanger comprises a first collecting pipeline, a second collecting pipeline, a plurality of refrigerant heat exchange flow paths which are connected with the first collecting pipeline and the second collecting pipeline in parallel, a gaseous refrigerant inlet and outlet and a plurality of communication channels, wherein the second collecting pipeline is divided into a plurality of collecting cavities, and the plurality of collecting cavities correspond to the plurality of communication channels one to one and are communicated with the gaseous refrigerant inlet and outlet through the corresponding communication channels; wherein the plurality of communicating channels satisfy at least one of the following conditions: the longer the communication channel, the larger the cross-sectional area of the through flow, and the smaller the number of refrigerant heat exchange flow paths communicated with the manifold corresponding to the longer communication channel. The utility model provides a technical scheme carries out optimal design to the second mass flow pipeline of heat exchanger, realizes that the subregion of the refrigerant in the second mass flow pipeline is drawn forth, has solved because the uneven problem of refrigerant flow distribution that the pressure drop difference leads to.

Description

Heat exchanger and air conditioner

Technical Field

The utility model relates to an air conditioning equipment field, concretely relates to heat exchanger and air conditioner.

Background

In the heat exchanger shown in fig. 1, in the evaporation condition, two-phase refrigerants (a gaseous refrigerant and a liquid refrigerant) flow in from the inlet collecting pipe on the lower side and then flow through the refrigerant heat exchange flow paths in the flat pipes, and the refrigerant exchanges heat with air when flowing in the flow path of the refrigerant heat exchanger and flows out from the outlet collecting pipe on the upper side after being changed into the gaseous refrigerant.

The import of heat exchanger is two-phase refrigerant, and the velocity of flow is low, and the export is gaseous refrigerant, and the velocity of flow is high, leads to along the flow direction (the direction from left to right in figure 1) of refrigerant in the export collecting flow pipeline, the pressure differential grow gradually at flat pipe both ends, so the flow difference through flat pipe also grow gradually, causes reposition of redundant personnel inequality and heat exchanger performance decay.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a heat exchanger and air conditioner aims at solving the refrigerant and divides the uneven, poor problem of heat exchanger performance of flow in the heat exchanger.

In order to achieve the above object, the heat exchanger provided by the present invention comprises a first collecting pipe, a second collecting pipe, and a plurality of parallel refrigerant heat exchange flow paths communicating the first collecting pipe and the second collecting pipe, wherein the heat exchanger further comprises a gaseous refrigerant inlet and outlet and a plurality of communication channels, the second collecting pipe is divided into a plurality of collecting chambers, the plurality of collecting chambers are in one-to-one correspondence with the plurality of communication channels, and the collecting chambers are communicated with the gaseous refrigerant inlet and outlet through the corresponding collecting chambers;

wherein a plurality of the communication passages satisfy at least one of the following conditions:

the longer the length of the communication channel, the larger the through-flow sectional area of the communication channel is, and the smaller the number of the refrigerant heat exchange flow paths communicated with the collecting cavities corresponding to the longer length of the communication channel is.

The utility model also provides an air conditioner, the air conditioner includes as above the heat exchanger.

The technical scheme of the utility model among, through separating into a plurality of manifolds with the second mass flow pipeline to every manifold realizes the intercommunication imported and exported with gaseous state refrigerant through a intercommunication passageway that corresponds, has realized that the gaseous state refrigerant of every mass flow intracavity draws forth alone through a intercommunication runner.

By adjusting the relative relation between the flow rate and the flow of the refrigerant in the communication channels, the larger the cross-sectional area of the communication channel with the longer length is, and/or the smaller the number of refrigerant heat exchange flow paths communicated with the manifold cavities corresponding to the communication channels with the longer length is, the pressure drop of the gaseous refrigerant in the communication channels can be adjusted when the gaseous refrigerant flows in the communication channels, so that the difference between the pressure drops of the gaseous refrigerant in the communication channels is smaller, and the pressure drops are all in a set range. The pressure drop difference in the plurality of communicating channels is small, so that the pressure difference between the inlet and the outlet of the plurality of refrigerant heat exchange flow paths is small, the refrigerant flow in the plurality of refrigerant heat exchange flow paths is balanced, the uniform distribution of the refrigerant is realized, and the heat exchange efficiency of the heat exchanger is improved.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings needed to be 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 diagram of a heat exchanger in some cases;

FIG. 2 is a schematic diagram of the temperature distribution of the heat exchanger of FIG. 1 in an evaporating condition;

fig. 3 is a schematic structural diagram of a heat exchanger according to an embodiment of the present invention;

FIG. 3a is an enlarged schematic view of the portion M in FIG. 3;

fig. 4 is a schematic partial structural view of a heat exchanger according to an embodiment of the present invention;

FIG. 5 is a schematic sectional view taken along line A-A of the heat exchanger of FIG. 4;

FIG. 6 is a schematic sectional view of the heat exchanger of FIG. 4 taken along line B-B;

FIG. 7 is a schematic cross-sectional view taken along line C-C of the heat exchanger of FIG. 4;

FIG. 8 is a schematic cross-sectional view taken along line D-D of the heat exchanger of FIG. 4;

FIG. 9 is a schematic cross-sectional view taken along line E-E of the heat exchanger of FIG. 4;

FIG. 10 is a schematic sectional view of the heat exchanger of FIG. 4 taken along line F-F;

FIG. 11 is a schematic sectional view of the heat exchanger of FIG. 4 taken along line G-G;

FIG. 12 is a schematic sectional view taken in the direction H-H of the heat exchanger of FIG. 4;

fig. 13 is a schematic structural diagram of a fin of a heat exchanger according to an embodiment of the present invention;

FIG. 14 is a perspective view of the fin of FIG. 13;

FIG. 15 is a partial structural view of the fin of FIG. 13;

FIG. 15a is an enlarged schematic view of the portion P in FIG. 15;

fig. 16 is a schematic structural view of a fin of a heat exchanger according to another embodiment of the present invention;

fig. 17 is a partial structural view of the fin of fig. 16.

The reference numbers illustrate:

reference numerals	Name (R)	Reference numerals	Name (R)
				100	Heat exchanger	1	Fin
10	Fin sub-sheet	11	A first collecting port
				12	Second collecting port	13	Refrigerant heat exchange flow path
14a-14d	Communication port	15a-15d	Communicating groove
				16	Communicating branch	17	Throttling groove
2	Gas refrigerant inlet and outlet	3	First collecting pipe
				4	Second collecting pipe	41a-41d	Manifold assembly
5a-5c	Partition board		6a-6d					Communicating channel
				61a-61d	First channel segment	62a-62d	Second channel segment

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

Detailed Description

The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts belong to the protection scope of the present invention.

It should be noted that all the directional indicators (such as up, down, left, right, front, back, etc.) in the embodiments of the present invention are only used to explain the relative position relationship between the components, the motion situation, etc. in a specific posture (as shown in fig. 4), and if the specific posture is changed, the directional indicator is changed accordingly.

In addition, descriptions in the present application as to "first", "second", and the like are for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicit to 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 application, unless expressly stated or limited otherwise, the terms "connected" and "fixed" are to be construed broadly, e.g., "fixed" may be fixedly connected or 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 meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.

In addition, the technical solutions between the embodiments of the present invention can be combined with each other, but it is necessary to be able to be realized by a person having ordinary skill in the art as a basis, and when the technical solutions are contradictory or cannot be realized, the combination of such technical solutions should be considered to be absent, and is not within the protection scope of the present invention.

In the heat exchanger 100 shown in fig. 1, if any structural improvement is not made on the inlet collecting pipe (i.e., the first collecting pipe 3) and the outlet collecting pipe (i.e., the second collecting pipe 4), the pressure difference between the inlet and the outlet of the flat pipe on the left side is small, so that the refrigerant flow is small, overheating is easy to occur (the color on the left side in fig. 2 indicates that the temperature is high), and the heat exchanger belongs to single-phase heat exchange and has poor heat exchange effect; the pressure difference between the inlet and the outlet of the flat pipe on the right side is large, the flow rate of the refrigerant is large, overheating does not occur (the color on the right side in figure 2 indicates that the temperature is low), the heat exchange is two-phase, and the heat exchange effect is good.

The heat exchanger 100 of fig. 1 has overall non-uniform flow and poor overall performance. One reason for the large right-side flow is that the refrigerant flowing from the left side is collected on the right side of the outlet collecting pipe, the total flow of the refrigerant is large, the flow rate is also large, the pressure drop on the right side is large, and the flow of the refrigerant in the flat pipe on the right side is larger than that of the refrigerant in the flat pipe on the left side, so that the refrigerant in the flat pipes on the left and right sides of the heat exchanger 100 is unevenly distributed, and the overall heat exchange effect is poor.

The embodiment of the utility model provides a heat exchanger 100 has solved the inhomogeneous problem of refrigerant distribution because the pressure drop difference arouses. The following description will take the heat exchanger 100 in the evaporating condition (i.e., the heat exchanger 100 is used as an evaporator) as an example. Of course, the heat exchanger 100 may also be used as a condenser.

Referring to fig. 3 and 5, in an embodiment of the present invention, the heat exchanger 100 includes a first collecting pipe 3, a second collecting pipe 4, and a plurality of parallel refrigerant heat exchanging flow paths 13 communicating the first collecting pipe 3 and the second collecting pipe 4. The heat exchanger 100 further comprises a gaseous refrigerant inlet and outlet 2 and a plurality of communication channels 6a-6d, the second collecting pipe 4 is divided into a plurality of collecting chambers 41a-41d, the plurality of collecting chambers 41a-41d correspond to the plurality of communication channels 6a-6d one by one, and the plurality of collecting chambers 41a-41d are communicated with the gaseous refrigerant inlet and outlet 2 through the corresponding communication channels 6a-6 d.

The plurality of communication passages 6a to 6d satisfy at least one of the following conditions:

the longer the communication passage, the larger the cross-sectional area of the flow passage, and the smaller the number of refrigerant heat exchange flow paths 13 communicated with the manifold chambers corresponding to the longer communication passage.

The heat exchanger 100 is used in an evaporation condition, that is, when the heat exchanger 100 is an evaporator, the second collecting pipe 4 communicated with the gaseous refrigerant inlet and outlet 2 is an outlet collecting pipe, and the first collecting pipe 3 is an inlet collecting pipe. The gaseous and liquid two-phase refrigerant can enter the heat exchanger 100 from the first collecting pipe 3 and then flow through the refrigerant heat exchange flow path 13, the refrigerant exchanges heat with air and evaporates when flowing through the refrigerant heat exchange flow path 13, and the evaporated gaseous refrigerant flows into the second collecting pipe 4 and finally flows out from the gaseous refrigerant inlet and outlet 2.

The second collecting pipe 4 is divided into a plurality of collecting chambers 41a-41d, and each collecting chamber is communicated with the gaseous refrigerant inlet and outlet 2 through a corresponding communication channel, so that the plurality of collecting chambers 41a-41d are communicated with the gaseous refrigerant inlet and outlet 2 through a plurality of communication channels 6a-6 d. Each manifold is communicated with the gaseous refrigerant inlet and outlet 2 through a corresponding communication channel, so that the gaseous refrigerant in each manifold is independently led out through a communication flow channel, and the mutual influence among the gaseous refrigerants in the plurality of manifolds 41a-41d is reduced.

The pressure drop of the gaseous refrigerant flowing in the communicating channel from the collecting cavity to the gaseous refrigerant inlet and outlet 2 is related to the through-flow sectional area S of the communicating channel, the length L of the communicating channel, the flow rate of the gaseous refrigerant (related to the flow rate of the gaseous refrigerant and the through-flow sectional area S of the communicating channel, and the flow rate of the gaseous refrigerant is related to the number N of the refrigerant heat exchange flow paths 13 communicated with the collecting cavity), by adjusting the relative relation between the flow rate and the flow path of the refrigerant in the communication channel, the longer the length of the communication channel is, the larger the through-flow sectional area of the communication channel is, and/or, the longer the communication channel, the less the number of the refrigerant heat exchange flow paths 13 communicated with the corresponding collecting cavity, the pressure drop of the gaseous refrigerant flowing in the communicating channels can be adjusted, so that the difference between the pressure drops of the gaseous refrigerant in the communicating channels 6a-6d is small, and the pressure drops are all in a set range. The pressure drop difference in the communication channels 6a to 6d is small, so that the pressure difference between the inlet and the outlet of the refrigerant heat exchange flow paths 13 is small, the refrigerant flow in the refrigerant heat exchange flow paths 13 is balanced, the uniform distribution of the refrigerant is realized, and the heat exchange efficiency of the heat exchanger 100 is improved.

The utility model discloses heat exchanger 100 according to the pressure drop characteristic of refrigerant, carries out optimal design to second mass flow pipeline 4, through separating into a plurality of manifold 41a-41d with second mass flow pipeline 4, realizes gaseous state refrigerant's subregion and draws forth, can improve because the refrigerant flow distribution inequality problem that the pressure drop difference leads to, has realized the evenly distributed of refrigerant, has promoted heat exchanger 100's performance.

It should be understood that the heat exchanger 100 may also be a condenser, which also facilitates uniform distribution of the refrigerant within the heat exchanger 100. The flow direction of the refrigerant in the condenser is opposite to the flow direction of the refrigerant in the evaporator, at this time, the first collecting pipe 3 of the heat exchanger 100 may be an outlet collecting pipe, the second collecting pipe 4 may be an inlet collecting pipe, and the gaseous refrigerant flows into the second collecting pipe 4 from the gaseous refrigerant inlet and outlet 2, then flows through the refrigerant heat exchange flow path 13 to exchange heat, and finally flows into the first collecting pipe 3.

In some exemplary embodiments, the number of manifolds and communication channels is N1, and N1 is a positive integer no less than 2.

Of the ith communicating channelCross-sectional area S of flow_iAnd length L_iThe number N of the refrigerant heat exchange flow paths 13 communicated with the collecting cavities corresponding to the ith communication channel_iThe relationship between them is:

N_i ²*L_i/S_i ^2.5k, where K is a set range and i is a positive integer no greater than N1.

By providing the flow cross-sectional area S of the ith communication passage_iLength L of the ith communication passage_iAnd the number N of refrigerant heat exchange flow paths 13 communicated with the ith collecting cavity corresponding to the ith communication channel_iSatisfies the following conditions: n is a radical of_i ²*L_i/S_i ^2.5K is a set range (which may be set experimentally or empirically), i.e., N_i ²*L_i/S_i ^2.5Within a set range, the pressure drop difference of the gaseous refrigerant in the plurality of communication channels is small, and within the set range, the pressure difference of the inlets and the outlets of the plurality of refrigerant heat exchange flow paths 13 is small and within the set range. The pressure difference between the inlet and the outlet of the multiple refrigerant heat exchange flow paths 13 is small, so that the refrigerant flow in the multiple refrigerant heat exchange flow paths 13 is balanced, the uniform distribution of the refrigerant is realized, and the heat exchange efficiency of the heat exchanger 100 is improved.

In some exemplary embodiments, at least one separator plate is disposed within the second manifold conduit 4, the at least one separator plate dividing the second manifold conduit 4 into a plurality of manifolds.

The second collecting pipe 4 is separated by arranging a partition plate, so that the mode of forming a plurality of collecting cavities is simple and easy to realize.

In some exemplary embodiments, as shown in fig. 4, three baffles 5a-5c are provided within the outlet manifold, with the three baffles 5a-5c separating the outlet manifold into four manifolds 41a-41d, i.e., 4 for N1. The four manifold chambers 41a-41d are communicated to the gaseous refrigerant inlet and outlet 2 through four communication channels 6a-6d, respectively. Of course, the number of the partition plates, the manifold and the communication passages is not limited to the foregoing, and may be set as desired.

Wherein the cross-sectional flow area S of the four communication passages 6a-6d₁-S₄Length L of₁-L₄And the number N of refrigerant heat exchange flow paths 13 communicating with the four manifolds 41a to 41d₁-N₄Satisfies the following conditions: n is a radical of₁ ²*L₁/S₁ ^2.5＝N₂ ²*L₂/S₂ ^2.5＝N₃ ²*L₃/S₃ ^2.5＝N₄ ²*L₄/S₄ ^2.5The pressure drop of the refrigerant in the four communication channels 6a to 6d is approximately equal, so that the pressure difference between the inlet and the outlet of the refrigerant heat exchange flow paths 13 is small, uniform distribution of the refrigerant in the refrigerant heat exchange flow paths 13 is facilitated, and the heat exchange efficiency of the heat exchanger 100 is improved.

In some exemplary embodiments, as the lengths of the communication channels are sequentially increased, the number of the refrigerant heat exchange flow paths 13 communicating with the manifolds corresponding to the communication channels is sequentially decreased.

Along with the sequential increase of the lengths of the communicating channels, the flow of the refrigerant in the collecting cavity corresponding to the communicating channels to the gaseous refrigerant inlet and outlet 2 is sequentially increased, the number of the refrigerant heat exchange flow paths 13 communicated with the collecting cavity corresponding to the communicating channels is sequentially reduced, and the relative relation between the flow of the refrigerant in the communicating channels and the flow is adjusted by the method, so that the pressure difference between two ends of the refrigerant heat exchange flow paths 13 is reduced, the refrigerant distribution uniformity is improved, and the performance of the heat exchanger 100 is improved.

In some exemplary embodiments, as shown in fig. 4, four collecting chambers 41a to 41d are sequentially disposed along the length direction of the second collecting pipe 4 (i.e., the left-right direction in fig. 4), and the gaseous refrigerant inlet/outlet 2 is disposed at one side of the second collecting pipe 4 along the length direction and is close to the collecting chamber 41 d. The lengths of the four communication passages 6a to 6d respectively communicating with the four manifolds 41a to 41d are sequentially reduced, and the number of the refrigerant heat exchange flow paths 13 communicating with the four manifolds 41a to 41d is sequentially increased.

In some exemplary embodiments, as shown in fig. 4, the length of the manifold communicated with the greater number of refrigerant heat exchange flow paths 13 is greater, and therefore, the lengths of the four manifolds 41a to 41d are sequentially increased.

In some exemplary embodiments, as shown in fig. 3, 3a, 13 and 14, the heat exchanger 100 further includes a plurality of fins 1 stacked one on another, and the fins 1 are provided with a first collecting port 11 and a second collecting port 12 at two ends, and a refrigerant heat exchanging flow path 13 communicating the first collecting port 11 and the second collecting port 12. The first collecting ports 11 of the plurality of fins 1 are sequentially connected to form a first collecting pipeline 3, and the second collecting ports 12 of the plurality of fins 1 are sequentially connected to form a second collecting pipeline 4.

The heat exchanger 100 is in a fin 1-collecting pipe integrated form, the fin 1 is vertically arranged, the fin 1 comprises a first collecting port 11 at the lower end, a second collecting port 12 at the upper end and one or more refrigerant heat exchange flow paths 13 formed by one or more thin pipe channels in the middle, the fin 1 forms the heat exchanger 100 in a laminated mode, the first collecting ports 11 on the fin 1 are connected in a laminated mode to form a first collecting pipe 3, and the second collecting ports 12 are connected in a laminated mode to form a second collecting pipe 4.

In some exemplary embodiments, as shown in fig. 15 and 15a, the fin 1 includes two fin sub-sheets 10, and the two fin sub-sheets 10 are attached and fixed (e.g., welded, etc.) to form the fin 1. The adjacent end surfaces of the two fin sub-pieces 10 are provided with concave parts, and the concave parts on the two fin sub-pieces 10 are matched to form a refrigerant heat exchange flow path 13.

The two fin sub-sheets 10 are respectively provided with a first sub-flow collecting port which penetrates through along the thickness direction, and the first sub-flow collecting ports on the two fin sub-sheets 10 are matched to form a first flow collecting port 11. At least one end of the peripheral wall of the first collecting port 11 protrudes out of the end face of the fin 1, so that the first collecting ports 11 of the plurality of fins 1 are connected in an inserted manner to form the first collecting pipeline 3.

The two fin sub-sheets 10 are respectively provided with a second sub-flow collecting port penetrating along the thickness direction, and the second sub-flow collecting ports on the two fin sub-sheets 10 are matched to form a second flow collecting port 12. At least one end of the peripheral wall of the second collecting port 12 protrudes out of the end face of the fin 1, so that the second collecting ports 12 of the plurality of fins 1 are connected in an inserted manner to form a second collecting pipeline 4.

In some exemplary embodiments, the separator is disposed in the second collecting port 12 such that a plurality of manifolds are sequentially disposed along the length direction of the second collecting pipe 4 (i.e., the stacking direction of the plurality of fins 1).

As shown in fig. 4, three separators 5a to 5c are respectively provided in the three second collecting ports 12 so as to divide the second collecting duct 4 into four collecting chambers 41a to 41d, and the four collecting chambers 41a to 41d are sequentially provided along the length direction of the second collecting duct 4 (i.e., the left-right direction in fig. 4).

In some exemplary embodiments, as shown in fig. 4, the plurality of fins 1 are disposed at equal intervals, and the gaseous refrigerant inlet/outlet 2 is disposed at one side (right side in fig. 4) of the second collecting pipe 4 along the length direction. The lengths of the plurality of manifolds are sequentially increased in a direction toward the gaseous refrigerant inlet/outlet 2 (i.e., in a direction from left to right in fig. 4), and the lengths of the communication passages corresponding to the manifolds are sequentially decreased.

As shown in fig. 4, the plurality of fins 1 are provided at equal intervals so that the length of the manifold communicated with the large number of refrigerant heat exchange passages 13 is increased. The lengths of the four communication passages 6a to 6d corresponding to the four manifolds 41a to 41d are sequentially reduced along the left-to-right direction, so that the number of the refrigerant heat exchange flow paths 13 communicated with the four manifolds 41a to 41d is sequentially increased, and the lengths of the four manifolds 41a to 41d are sequentially increased.

In some exemplary embodiments, the communication channel includes a first channel section disposed along the length direction of the fin 1 and a second channel section disposed along the length direction of the second collecting pipe 4, the first channel section communicates with the second channel section, and the other end of the first channel section communicates with the collecting chamber, and the other end of the second channel section communicates with the gaseous refrigerant inlet/outlet 2.

As shown in fig. 4, the communication channel 6a includes a first channel section 61a arranged along the length direction of the fin 1 (i.e., the up-down direction in fig. 4) and a second channel section 62a arranged along the length direction of the second collecting pipe 4 (i.e., the left-right direction in fig. 4), the first channel section 61a is arranged vertically, the second channel section 62a is arranged horizontally, the first channel section 61a communicates with the second channel section 62a, and the formed communication channel 6a has an L shape. The other end (lower end in fig. 4) of the first passage section 61a communicates with the manifold 41a, and the other end (right end in fig. 4) of the second passage section 62a communicates with the gaseous refrigerant inlet/outlet 2.

Similarly, the communication channel 6b is L-shaped, and includes a vertical first channel section 61b arranged along the length direction of the fin 1 and a horizontal second channel section 62b arranged along the length direction of the second collecting pipe 4, the other end of the first channel section 61b is communicated with the manifold 41b, and the other end of the second channel section 62b is communicated with the gaseous refrigerant inlet/outlet 2.

The communication channel 6c is L-shaped and comprises a vertical first channel section 61c arranged along the length direction of the fin 1 and a horizontal second channel section 62c arranged along the length direction of the second collecting pipe 4, the other end of the first channel section 61c is communicated with the collecting cavity 41c, and the other end of the second channel section 62c is communicated with the gaseous refrigerant inlet and outlet 2.

The communicating channel 6d is L-shaped and comprises a vertical first channel section 61d arranged along the length direction of the fin 1 and a horizontal second channel section 62d arranged along the length direction of the second collecting pipe 4, the other end of the first channel section 61d is communicated with the collecting cavity 41d, and the other end of the second channel section 62d is communicated with the gaseous refrigerant inlet and outlet 2.

The lengths of the first channel segments 61a-61d decrease in sequence and the lengths of the second channel segments 62a-62d decrease in sequence, so that the lengths of the communication channels 6a-6d decrease in sequence.

In some exemplary embodiments, the plurality of fins 1 between the first channel section and the gaseous refrigerant inlet/outlet 2 are all provided with communication ports penetrating along the thickness direction, and the communication ports on the plurality of fins 1 are sequentially connected to form a second channel section. A communication groove for communicating the communication port with the second collecting port 12 is formed in a part of the plurality of fins 1 corresponding to the manifold, and the communication groove forms a first passage section. The fin 1 is provided with a communication port, a communication groove, a second collecting port 12, a refrigerant heat exchange flow path 13, and a first collecting port 11 in this order along the longitudinal direction of the fin 1.

As shown in fig. 4 to 12, the plurality of fins 1 (i.e., the plurality of fins 1 on the right side of the first passage section 61 a) between the first passage section 61a and the gaseous refrigerant inlet/outlet 2 are each provided with a communication port 14a penetrating the fin 1 in the thickness direction, and the communication ports 14a of the plurality of fins 1 are connected in sequence to form a second passage section 62 a. The plurality of communication ports 14a form the second passage section 62a in a similar manner to the plurality of first sub-manifold ports form the first manifold port 11 and the plurality of second sub-manifold ports form the second manifold port 12. As shown in fig. 4 and 5, among the plurality of fins 1 corresponding to the manifold 41a, a communication groove 15a for communicating the communication port 14a with the second manifold port 12 is provided in a part of the fins 1 (e.g., one or more fins 1), and the communication groove 15a forms a first passage section 61 a.

As shown in fig. 4 and 7 to 12, the plurality of fins 1 (i.e., the plurality of fins 1 on the right side of the first passage section 61 b) between the second passage section 61b and the gaseous refrigerant inlet/outlet 2 are each provided with a communication port 14b penetrating the fin 1 in the thickness direction, and the communication ports 14b of the plurality of fins 1 are connected in sequence to form a second passage section 62 b. As shown in fig. 4 and 7, among the plurality of fins 1 corresponding to the manifold 41b, a communication groove 15b for communicating the communication port 14b with the second manifold port 12 is provided in a part of the fins 1 (e.g., one or more fins 1), and the communication groove 15b forms a first passage section 61 b.

As shown in fig. 4 and 9 to 12, the plurality of fins 1 (i.e., the plurality of fins 1 on the right side of the first passage section 61 c) between the second passage section 61c and the gas refrigerant inlet/outlet 2 are each provided with a communication port 14c penetrating the fin 1 in the thickness direction, and the communication ports 14c of the plurality of fins 1 are connected in sequence to form a second passage section 62 c. As shown in fig. 4 and 9, among the plurality of fins 1 corresponding to the manifold 41c, a communication groove 15c for communicating the communication port 14c with the second manifold port 12 is provided in a part of the fins 1 (e.g., one or more fins 1), and the communication groove 15c forms a first passage section 61 c.

As shown in fig. 4, 11, and 12, the plurality of fins 1 (i.e., the plurality of fins 1 on the right side of the first passage section 61 d) between the second passage section 61d and the gas refrigerant inlet/outlet 2 are each provided with a communication port 14d penetrating the fin 1 in the thickness direction, and the communication ports 14d of the plurality of fins 1 are connected in sequence to form a second passage section 62 d. As shown in fig. 4 and 11, among the plurality of fins 1 corresponding to the manifold 41d, a communication groove 15d for communicating the communication port 14d with the second manifold port 12 is provided in a part of the fins 1 (e.g., one or more fins 1), and the communication groove 15d forms a first passage section 61 d.

As shown in fig. 5 to 12, the fin 1 includes communication ports 14a to 14d (if any), one of the communication grooves 15a to 15d (if any), a second collecting port 12, a refrigerant heat exchange flow path 13, and a first collecting port 11, which are provided in this order from top to bottom along the longitudinal direction of the fin 1. The communication grooves 15a to 15d may be groove bodies arranged vertically. The communication channels 15a-15d may be channel bodies with a circular (or other) cross-section, so that the first channel segments 61a-61d may be channels with a circular through-flow cross-section. The communication ports 14a-14d may be circular (or other shapes) such that the second channel segments 62a-62d may be channels that are circular in cross-section.

In some exemplary embodiments, the flow cross-sectional areas of the first channel segments of the plurality of communication channels are equal. As shown in fig. 4, the first passage sections 61a to 61d of the four communication passages 6a to 6d have the same cross-sectional flow area, that is, the circular communication ports 14a to 14d have the same hole diameter, which facilitates the processing of the communication ports.

In some exemplary embodiments, the flow cross-sectional areas of the second channel segments of the plurality of communication channels are equal. As shown in fig. 4, any of the second channel segments 62a-62d of the four communication channels 6a-6d may be formed by communication grooves 15a-15d formed by fitting recesses opened on the adjacent end faces of the two fin sub-pieces 10 of one fin 1. The cross-sectional flow areas of the second channel segments 62a-62d are all equal, facilitating the machining of the second channel segments 62a-62 d.

In some exemplary embodiments, the first and second channel segments of at least one of the plurality of communication channels are equal in cross-sectional flow area.

As shown in fig. 4, the first passage section 61a and the second passage sections 62a to 62d of the communication passage 6a are equal in flow cross-sectional area, the first passage section 61b and the second passage section 62b of the communication passage 6b are equal in flow cross-sectional area, the first passage section 61c and the second passage section 62c of the communication passage 6c are equal in flow cross-sectional area, and the first passage section 61d and the second passage section 62d of the communication passage 6d are equal in flow cross-sectional area.

In some exemplary embodiments, the cross-sectional flow area of the first and second channel segments of all of the communication channels is equal. As shown in FIG. 4, the first passage sections 61a to 61d and the second passage sections 62a to 62d of the four communication passages 6a to 6d are equal in cross-sectional flow area.

Of course, the flow-through cross-sectional areas of the first passage segments 61a-61d of the plurality of communication passages 6a-6d may not be equal, or the flow-through cross-sectional areas of the second passage segments 62a-62d of the plurality of communication passages 6a-6d may not be equal. The cross-sectional flow area of any of the communication passages 6a-6d may remain constant along its length or, alternatively, may vary.

In some exemplary embodiments, the location of the communication of any one of the manifolds 41a-41d with the corresponding communication channel 6a-6d is located at the center of the length of the manifold. Of course, the communicating portion between the manifold and the corresponding communicating channel may be disposed off the center of the length direction of the manifold, such as on the left side (the side far from the gaseous refrigerant inlet/outlet 2) or on the right side (the side near to the gaseous refrigerant inlet/outlet 2).

In some exemplary embodiments, as shown in fig. 3 and fig. 3a, the heat exchanger 100 includes two first collecting pipes 3, and the two first collecting pipes 3 communicate with each other through a throttling channel, wherein one first collecting pipe 3 is used as an inlet of a two-phase refrigerant into the heat exchanger 100, and the other first collecting pipe 3 communicates with the refrigerant heat exchange flow path 13.

As shown in fig. 13 and 14, each of the plurality of fins 1 of the heat exchanger 100 has two first collecting ports 11, and the two first collecting ports 11 communicate with each other through the throttle groove 17. One first current collecting port 11 on the plurality of fins 1 is communicated to form one first current collecting pipeline 3, the other first current collecting port 11 on the plurality of fins 1 is communicated to form the other first current collecting pipeline 3, and throttling grooves 17 on the plurality of fins 1 form throttling channels communicated with the two first current collecting pipelines 3.

In some exemplary embodiments, the heat exchanger 100 includes two second manifold conduits 4, with communication between the two second manifold conduits 4.

In some exemplary embodiments, as shown in fig. 16 and 17, a plurality of refrigerant heat exchange flow paths 13 are provided on the fin 1, and different refrigerant heat exchange flow paths 13 are communicated with each other through a communication branch 16.

The heat exchanger 100 shown in fig. 16 and 17 is in a condensing mode (i.e., the heat exchanger 100 is used as a condenser), and the uppermost downward arrow in the figure indicates the flow direction of the wind, and the other arrows indicate the flow direction of the refrigerant. In the condensation working condition, the gaseous refrigerant flows along the refrigerant heat exchange flow path 13 and is condensed, the liquid film is gradually thickened, the thermal resistance is increased, and the heat transfer effect is weakened; after encountering the communicating branch 16, the communicating branch 16 can play a role of draining off the condensate under the action of the surface tension of the condensate, thereby reducing the thickness of a liquid film, reducing the thermal resistance of the condensate and strengthening the condensation heat exchange. Because the heat exchange effect of the windward side (the upper side in fig. 16 and 17 is the windward side) is good, the condensation rate is high, the arrangement of the communication branch 16 can enable the condensate to move from the refrigerant heat exchange flow path 13 of the windward side to the leeward side (the lower side in fig. 16 and 17 is the leeward side) along the communication branch 16, and the windward side can also keep good heat exchange effect.

In the evaporation mode (i.e., the heat exchanger 100 is used as an evaporator), the refrigerant moves in the refrigerant heat exchange flow path 13 in the opposite direction to that in the condensation mode. Because the refrigerant in the refrigerant heat exchange flow path 13 on the windward side has good heat exchange, high evaporation rate, high dryness, high flow rate and low local static pressure, and the refrigerant heat exchange flow path 13 on the leeward side has relatively high local static pressure, the refrigerant moves to the windward side under the action of pressure difference, and the heat exchange effect on the windward side is improved.

The multiple refrigerant heat exchange flow paths 13 on the fin 1 of the heat exchanger 100 are communicated with each other through the communication branch 16, so that the refrigerants in the multiple refrigerant heat exchange flow paths 13 can flow mutually, the heat exchange process is adapted, the refrigerant flow in the refrigerant heat exchange flow paths 13 is automatically adjusted and distributed, and the heat exchange efficiency is improved.

In some exemplary embodiments, as shown in fig. 16 and 17, a plurality of refrigerant heat exchange flow paths 13 are sequentially arranged on the fin 1 along the width of the fin 1, and the communication branch 16 is arranged between adjacent refrigerant heat exchange flow paths 13, that is, the adjacent refrigerant heat exchange flow paths 13 are communicated through the communication branch 16.

As shown in fig. 16 and 17, the refrigerant heat exchange flow path 13 may include two arc-shaped segments and two straight-line segments connecting the two arc-shaped segments, the two arc-shaped segments are respectively communicated with the first collecting pipe 3 and the second collecting pipe 4, the straight-line segments of the plurality of refrigerant heat exchange flow paths 13 may be arranged in parallel, and the communication branch 16 may connect the straight-line segments of two adjacent refrigerant heat exchange flow paths 13.

It should be understood that the form of the refrigerant heat exchanging flow path 13 is not limited to the above, for example, the refrigerant heat exchanging flow path 13 may include no arc segment, only a straight segment, only an arc segment and a straight segment at one end, or other shapes.

In some exemplary embodiments, as shown in fig. 16 and 17, the communication branch 16 is disposed perpendicular to a straight line section of the refrigerant heat exchange flow path 13.

In some exemplary embodiments, as shown in fig. 16 and 17, the communication branch 16 is disposed at a side close to the first collecting pipe 3, and the communication branch 16 starts from 50% to 60% of the total length of the refrigerant heat exchanging flow path 13 from the second collecting pipe 4. Namely, the communicating branch 16 is arranged between the adjacent refrigerant heat exchange flow paths 13 from the position 50% -60% of the total length of the refrigerant heat exchange flow paths 13 away from the second collecting pipe 4.

The communication branch 16 is arranged on one side, and from the view of the condensation working condition, the initial setting position of the communication branch 16 is 50% -60% of the total length of the refrigerant heat exchange flow path 13, condensate begins to exist at 50% -60% of the total length of the refrigerant heat exchange flow path 13, and the communication branch 16 is arranged at the position where the condensate exists, so that the effect of heat transfer enhancement can be achieved.

In some exemplary embodiments, the tube diameter of the communicating leg 16 does not exceed the spacing between adjacent fins 1 so as not to cause a significant air-side pressure drop if condensate drainage is enabled.

In some exemplary embodiments, as shown in fig. 16 and 17, the communication branches 16 connected between two adjacent refrigerant heat exchange flow paths form a row, a plurality of communication branches 16 located in the same row are provided, and the distance between adjacent communication branches 16 located in the same row decreases in the direction close to the first collecting pipe 3, that is, the arrangement of the communication branches 16 gradually increases.

The gaps between the communicating branches 16 are gradually encrypted along the flow direction of the refrigerant under the condensation working condition, so that gas-liquid separation can be more effectively realized, and the heat exchange effect is enhanced.

In some exemplary embodiments, as shown in fig. 16 and 17, the communicating branches 16 are arranged in a plurality of rows, and the communicating branches 16 of adjacent two rows are staggered.

In the heat exchanger 100 shown in fig. 16 and 17, after the communicating branch 16 is provided between the plurality of refrigerant heat exchange flow paths 13 on the fin 1, a water flowing test in the tube is performed on the heat exchanger 100, and test data shows that the heat transfer efficiency of the heat exchanger 100 is improved by about 50%.

In the embodiment shown in fig. 3-17, the heat exchanger 100 is a fin 1-collecting pipe integrated structure, but of course, the heat exchanger 100 may also be a common microchannel heat exchanger 100, for example, the heat exchanger 100 shown in fig. 1 may be configured by modifying an outlet collecting pipe on the upper side thereof, disposing a partition plate on the outlet collecting pipe to form a plurality of collecting chambers, and communicating the plurality of collecting chambers with the gaseous refrigerant inlet and outlet 2 by using a plurality of communicating channels. And a communication branch 16 can be arranged among the refrigerant heat exchange flow paths 13 in the flat tubes so as to automatically adjust and distribute the refrigerant flow in the refrigerant heat exchange flow paths 13 and improve the heat exchange efficiency.

The embodiment of the utility model provides a still provide an air conditioner, including foretell heat exchanger 100.

The above only is the preferred embodiment of the present invention, not so limiting the patent scope of the present invention, all under the concept of the present invention, the equivalent structure transformation made by the contents of the specification and the drawings is utilized, or the direct/indirect application is included in other related technical fields in the patent protection scope of the present invention.

Claims

1. A heat exchanger comprises a first collecting pipeline, a second collecting pipeline and a plurality of refrigerant heat exchange flow paths which are arranged in parallel and communicated with the first collecting pipeline and the second collecting pipeline, and is characterized by further comprising a gaseous refrigerant inlet and outlet and a plurality of communication channels, wherein the second collecting pipeline is divided into a plurality of collecting chambers, the plurality of collecting chambers are in one-to-one correspondence with the plurality of communication channels and are communicated with the gaseous refrigerant inlet and outlet through the corresponding communication channels;

2. The heat exchanger of claim 1 wherein at least one baffle is disposed within said second manifold conduit, at least one of said baffles dividing said second manifold conduit into a plurality of said manifolds.

3. The heat exchanger of claim 1, wherein the number of said manifolds and said communication passages is N1, N1 is a positive integer no less than 2;

cross-sectional flow area S of the ith communication passage_iAnd length L_iAnd the number N of the refrigerant heat exchange flow paths communicated with the collecting cavities corresponding to the ith communication channels_iThe relationship between them is:

4. The heat exchanger as claimed in claim 2, wherein the heat exchanger further comprises a plurality of fins stacked on each other, the fins are provided with a first collecting port and a second collecting port at both ends, and the refrigerant heat exchange flow path communicating the first collecting port and the second collecting port,

the fin is characterized in that the first collecting ports of the plurality of fins are sequentially connected to form the first collecting pipeline, the second collecting ports of the plurality of fins are sequentially connected to form the second collecting pipeline, the partition plate is arranged in the second collecting ports, and the plurality of collecting cavities are sequentially arranged along the length direction of the second collecting pipeline.

5. The heat exchanger as claimed in claim 4, wherein a plurality of the fins are arranged at equal intervals, and the gaseous refrigerant inlet and outlet are arranged at one side of the second collecting pipe along the length direction;

the lengths of the plurality of collecting cavities are sequentially increased along the direction close to the gaseous refrigerant inlet and outlet, and the lengths of the communicating channels corresponding to the collecting cavities are sequentially decreased.

6. The heat exchanger as claimed in claim 5, wherein the communication channel includes a first channel section disposed along a length direction of the fin and a second channel section disposed along a length direction of the second collecting pipe, the first channel section communicates with the second channel section, and the other end of the first channel section communicates with the manifold, and the other end of the second channel section communicates with the gaseous refrigerant inlet/outlet.

7. The heat exchanger as claimed in claim 6, wherein the plurality of fins between the first channel section and the gaseous refrigerant inlet/outlet are each provided with a communication port penetrating in a thickness direction, and the communication ports of the plurality of fins are sequentially connected to form the second channel section;

a part of the fins corresponding to the collecting cavity are provided with communicating grooves which are communicated with the communicating ports and the second collecting port, and the communicating grooves form the first channel section;

the communication port, the communication groove, the second collecting port, the refrigerant heat exchange flow path and the first collecting port are sequentially arranged along the length direction of the fin.

8. The heat exchanger of claim 6, wherein the first channel segments of the plurality of communication channels are of equal cross-sectional flow area;

and/or the flow cross-sectional areas of the second channel segments of the plurality of communication channels are equal;

and/or the flow cross-sectional area of the first channel section and the second channel section of at least one of the communication channels is equal in the plurality of communication channels.

9. The heat exchanger of any one of claims 1 to 8, wherein the heat exchanger is an evaporator, the first collecting conduit is an inlet collecting conduit, and the second collecting conduit is an outlet collecting conduit;

or the heat exchanger is a condenser, the first collecting pipeline is an outlet collecting pipeline, and the second collecting pipeline is an inlet collecting pipeline.

10. An air conditioner characterized by comprising the heat exchanger according to any one of claims 1 to 9.