CN216953290U - Heat exchanger and air conditioner - Google Patents
Heat exchanger and air conditioner Download PDFInfo
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- CN216953290U CN216953290U CN202220528963.9U CN202220528963U CN216953290U CN 216953290 U CN216953290 U CN 216953290U CN 202220528963 U CN202220528963 U CN 202220528963U CN 216953290 U CN216953290 U CN 216953290U
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- 238000004781 supercooling Methods 0.000 claims abstract description 120
- 239000007788 liquid Substances 0.000 claims abstract description 53
- 238000000926 separation method Methods 0.000 abstract description 5
- 238000010257 thawing Methods 0.000 abstract description 4
- 238000009826 distribution Methods 0.000 description 13
- 230000000694 effects Effects 0.000 description 8
- 239000003507 refrigerant Substances 0.000 description 8
- 238000010438 heat treatment Methods 0.000 description 4
- 238000004378 air conditioning Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000017525 heat dissipation Effects 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000006185 dispersion Substances 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
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Abstract
The utility model provides a heat exchanger and an air conditioner, wherein a body of the heat exchanger is alternately distributed with a common heat exchange area and a supercooling heat exchange area vertical to a heat exchange wind direction; the common heat exchange area is composed of at least one section of common heat exchange section, and the supercooling heat exchange area is composed of at least one section of supercooling heat exchange section. The utility model can solve the problem of uneven liquid separation and heat exchange of the flow path of the heat exchanger, the supercooling heat exchange section can not block the heat exchange of the common heat exchange section, and the uniformity of liquid separation and heat exchange of each flow path is ensured. Due to the fact that the supercooling heat exchange sections are more effectively dispersed, the influence of uneven air quantity on heat exchange is prevented, and defrosting efficiency of the heat exchanger under the external working condition that frosting is easy to occur is improved. In addition, the shunting point and the converging point of the heat exchange pipeline are connected by adopting a Y-shaped tee joint, so that the pipeline can be effectively simplified, and the cost is reduced.
Description
Technical Field
The utility model relates to the technical field of air conditioners, in particular to a heat exchanger and an air conditioner.
Background
The heat exchanger is one of important parts of an air conditioning and refrigerating system. In the design of an air conditioning system, in addition to the selection of the size of the heat exchanger, the distribution design of the flow paths of the heat exchanger is also very important. In the prior art, in order to improve the heat exchange amount and reduce the system pressure drop, the total supercooling heat exchange section of the heat exchanger is generally divided into a plurality of supercooling heat exchange sections to different positions of the heat exchanger; in the flow scheme shown in fig. 1, there are 3 rows of heat exchange tubes, and 3 supercooling heat exchange sections are divided from one row of the windward side P1, P2 and P3, and the rest of heat exchange tubes are common heat exchange sections. The scheme can improve the supercooling degree and the refrigerating capacity of the system, and can avoid the problems of overhigh flow speed, insufficient heat exchange and increased pressure drop of the refrigerant caused by the fact that all branches are converged into one path for supercooling.
However, 3 supercooling heat exchange sections in the scheme are concentrated on the windward side and are arranged in a row for heat exchange, the heat exchange effect of the common heat exchange section can be influenced, the supercooling heat exchange section can block the heat exchange between the common heat exchange section on the leeward side and the wind, and the liquid separation and heat exchange of the flow path of the heat exchanger are not uniform. This negative effect is also amplified when uneven wind field distribution is encountered.
SUMMERY OF THE UTILITY MODEL
In view of the above, the utility model provides a heat exchanger and an air conditioner, which can solve the problem of uneven liquid and heat separation and exchange of a flow path of the heat exchanger.
The utility model provides a heat exchanger, wherein a body of the heat exchanger is alternately distributed with a common heat exchange area and a supercooling heat exchange area vertical to a heat exchange wind direction;
the common heat exchange area is composed of at least one section of common heat exchange section, and the supercooling heat exchange area is composed of at least one section of supercooling heat exchange section.
Preferably, the sub-cooling heat exchange areas are connected in parallel.
Preferably, the supercooling heat exchange area comprises a first supercooling heat exchange section and a second supercooling heat exchange section which are connected in parallel.
Preferably, the common heat transfer zones are connected in parallel.
Preferably, the common heat exchange zone comprises a first common heat exchange section and a second common heat exchange section connected in parallel.
Preferably, each sub-cooling heat exchange section is connected with at least one common heat exchange section in series.
Preferably, the heat exchanger is provided with a main liquid inlet pipeline and a main liquid outlet pipeline;
a liquid outlet of the main liquid inlet pipeline is connected with the common heat exchange sections of the common heat exchange areas;
a liquid inlet of the main liquid outlet pipeline is connected with the supercooling heat exchange sections of the supercooling heat exchange areas, and a liquid outlet of the main liquid outlet pipeline is connected with the throttling device;
at least one row of common heat exchange sections are arranged in the common heat exchange area facing the heat exchange wind direction, and at least one row of supercooling heat exchange sections are arranged in the supercooling heat exchange area facing the heat exchange wind direction.
Preferably, the common heat exchange section has the same pipe distribution specification, or the supercooling heat exchange section has the same pipe distribution specification.
Preferably, the shunting point and the converging point of the heat exchange pipeline of the heat exchanger are connected by adopting a Y-shaped tee joint.
The utility model has the beneficial effects that: the supercooling heat exchange section can not block the heat exchange of the common heat exchange section, the uniformity of liquid-separating heat exchange of each flow path is ensured, and the influence of uneven air volume on the heat exchange is prevented due to more effective dispersion of the supercooling heat exchange section; the shunting point and the converging point of the heat exchange pipeline are connected by adopting a Y-shaped tee joint, so that the pipeline can be effectively simplified and the cost is reduced; under the external working condition that the frosting is easy to occur, the flow path distribution structure of the heat exchanger can improve the defrosting efficiency and improve the energy efficiency.
Drawings
The utility model is described in detail below with reference to examples and figures, in which:
fig. 1 is a piping diagram of a heat exchanger of prior art solution 1.
Fig. 2 is a piping diagram of the heat exchanger of prior art solution 2.
Fig. 3 is a piping diagram of the heat exchanger of the present invention.
FIG. 4 is a schematic view of a piping scheme of the first embodiment of the present invention.
FIG. 5 is a schematic view of a piping scheme of a second embodiment of the present invention.
FIG. 6 is a schematic view of a third embodiment of the present invention.
Detailed Description
In order to make the technical problems, technical solutions and advantageous effects to be solved by the present invention more clearly apparent, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the utility model and are not intended to limit the utility model.
Thus, a feature indicated in this specification will serve to explain one of the features of one embodiment of the utility model, and does not imply that every embodiment of the utility model must have the stated feature. Further, it should be noted that this specification describes many features. Although some features may be combined to show a possible system design, these features may also be used in other combinations not explicitly described. Thus, the combinations illustrated are not intended to be limiting unless otherwise specified.
The principles of the present invention will be described in detail below with reference to the accompanying drawings and embodiments.
Fig. 1 shows a prior art scheme, in which a heat exchange flow path is divided into 3 heat exchange branches L1, L2 and L3, wherein the L1 branch includes an M1 ordinary heat exchange section and a P1 supercooling heat exchange section; the L2 branch comprises an M2 common heat exchange section and a P2 supercooling heat exchange section; the L3 branch comprises an M3 common heat exchange section and a P3 supercooling heat exchange section. The drawbacks of this solution are: because three supercooling heat exchange sections P1, P2 and P3 are concentrated on one row at the windward side for heat exchange, the heat exchange between the ordinary heat exchange section at the leeward side and the wind is blocked, the heat dissipation of part of the ordinary heat exchange sections is influenced, and the liquid separation and heat exchange are not uniform. This negative effect is also amplified when uneven wind field distribution is encountered.
Fig. 2 shows another prior art scheme, in the scheme, 4 heat exchange branches including L1, L2, L3, and L4 are arranged on a heat exchanger, each heat exchange branch is divided into two parallel common heat exchange sections, and then the total of 8 common heat exchange sections are converged and mixed to enter a total supercooling heat exchange section P. After heat exchange is completed in the total supercooling heat exchange section P, the refrigerant flows to the throttling device through the total liquid outlet pipe 2.
In the scheme, 8 common heat exchange sections are concentrated on the upper part of the heat exchanger to form a common heat exchange area 110, the total supercooling heat exchange section P forms an overcooling heat exchange area 210 at the bottom of the heat exchanger, and heat exchange air flows through the heat exchanger from the right side and exchanges heat with the common heat exchange area 110 and the overcooling heat exchange area 210.
The drawbacks of this solution are: the supercooling heat exchange sections of the heat exchanger are all concentrated at one position, so that supercooling heat exchange is too concentrated, and the heat dissipation effect can be seriously influenced when the heat exchange environment is influenced. In addition, the supercooling heat exchange section of the scheme has large pressure difference and high flow speed, so that the supercooling effect cannot be fully exerted.
In order to solve the problems of uneven liquid-separating heat exchange and poor supercooling heat exchange effect of the flow path of the heat exchanger in the prior art, the utility model provides a novel heat exchanger, and aims to improve the pipe arrangement and the flow path of the heat exchanger in the prior art.
The utility model provides a heat exchanger as shown in fig. 3, wherein the heat exchange wind direction moves from the right side to the left side of the heat exchanger, common heat exchange areas and supercooling heat exchange areas are alternately distributed on the body of the heat exchanger perpendicular to the heat exchange wind direction, and the heat exchanger sequentially comprises a first common heat exchange area 110, a first supercooling heat exchange area 210, a second common heat exchange area 120, a second supercooling heat exchange area 220, a third common heat exchange area 130 and a third supercooling heat exchange area 230 from top to bottom.
The first common heat exchange zone 110 is composed of a common heat exchange section M1, the first supercooling heat exchange zone 210 is composed of a supercooling heat exchange section P1, the second common heat exchange zone 120 is composed of a common heat exchange section M2, the second supercooling heat exchange zone 220 is composed of a supercooling heat exchange section P2, the third common heat exchange zone 130 is composed of a common heat exchange section M3, and the second supercooling heat exchange zone 230 is composed of a supercooling heat exchange section P3.
The ordinary heat exchange sections M1, M2 and M3 and the supercooling heat exchange sections P1, P2 and P3 are coiled on the heat exchanger body. The pipe distribution distance and the pipe diameters of all sections can be adjusted according to the shape of the heat exchanger body and the specific air volume of all parts of the heat exchanger body. The optimal pipe distribution scheme is that the common heat exchange sections adopt uniform pipe distribution specifications, and the supercooling heat exchange sections also adopt uniform pipe distribution specifications, namely the pipe distribution diameters, materials, densities and trends of the common heat exchange sections M1, M2 and M3 are the same, and the pipe distribution diameters, materials, densities and trends of the supercooling heat exchange sections P1, P2 and P3 are the same, so that the pressure, the refrigerant flow rate and the temperature of each heat dissipation flow path are more balanced.
In this embodiment, the common heat exchange zones are connected in parallel, the supercooling heat exchange zones are also connected in parallel, and each supercooling heat exchange section is connected in series with at least one common heat exchange section. Specifically, the ordinary heat exchange section M1 is connected in series with the supercooling heat exchange section P1, the ordinary heat exchange section M2 is connected in series with the supercooling heat exchange section P2, the ordinary heat exchange section M3 is connected in series with the supercooling heat exchange section P3, and the rest is done in sequence; in addition, all the supercooling heat exchange sections including P1, P2 and P3 are connected in parallel, and during heat exchange, refrigerant flows to the supercooling heat exchange sections through the common heat exchange sections and flows to the throttling device after converging.
In addition, because the supercooling heat exchange section is more effectively dispersed, the influence of uneven heat exchange air quantity on supercooling heat exchange is reduced.
Example 1
The embodiment shown in fig. 4 is provided for the specific tube arrangement mode of the heat exchanger.
In this embodiment, the heat exchanger is divided into 4 heat exchange areas from top to bottom, including the first common heat exchange area 110, the first supercooling heat exchange area 210, the second common heat exchange area 120, and the second supercooling heat exchange area 220. The common heat exchange area is formed by common heat exchange section pipe arrangement, and the supercooling heat exchange area is formed by supercooling heat exchange section pipe arrangement.
In this embodiment, the specifications of the common heat exchange sections of each common heat exchange zone are the same, and each common heat exchange section includes a first common heat exchange section a1, a second common heat exchange section a2, a third common heat exchange section A3, and a fourth common heat exchange section a4, which are connected in parallel. The specification of the supercooling heat exchange section of each supercooling heat exchange zone is the same, and the supercooling heat exchange zone comprises a first supercooling heat exchange section B1 and a second supercooling heat exchange section B2 which are connected in parallel. The first common heat exchange section A1 and the second common heat exchange section A2 are converged and then connected in series with the first supercooling heat exchange section B1, and the third common heat exchange section A3 and the fourth common heat exchange section A4 are converged and then connected in series with the second supercooling heat exchange section B2.
Because each supercooling heat exchange region is connected with two supercooling heat exchange sections with different flow paths in parallel, if the first supercooling heat exchange region 210 comprises the first supercooling heat exchange section B1 and the second supercooling heat exchange section B2, the installation cost of the supercooling heat exchange sections can be reduced under the condition of not influencing the whole heat exchange effect.
In this embodiment, the heat exchanger is provided with a total liquid inlet pipeline 1 and a total liquid outlet pipeline 2, a liquid outlet of the total liquid inlet pipeline 1 is connected with a liquid inlet of each common heat exchange section, a liquid inlet of the total liquid outlet pipeline 2 is connected with a liquid outlet of each supercooling heat exchange section, and a liquid outlet of the total liquid outlet pipeline 2 is connected with the throttling device.
In order to improve the heat exchange capacity of the heat exchanger, two rows of common heat exchange sections are distributed on each common heat exchange area in a staggered mode facing hot air exchange, and two rows of supercooling heat exchange sections are distributed on each supercooling heat exchange area in a staggered mode facing hot air exchange.
Three rows of common heat exchange sections and supercooling heat exchange sections can be further arranged according to requirements. No matter the increase and decrease of the number of rows of the distributed tubes are changed, the common heat exchange areas and the supercooling heat exchange areas are always expanded or reduced in occupied space along the heat exchange wind direction, and the condition that the supercooling heat exchange sections and the common heat exchange sections block heat exchange air flow is avoided.
When the heat exchange is carried out in the air conditioner refrigeration mode, the heat exchange air passes through the heat exchanger from the right side to move to the left side, and the supercooling heat exchange area and the common heat exchange area cannot be shielded mutually, so that the uniform heat exchange can be realized, and the problem that the heat exchange cannot be completely carried out due to the uneven air volume of a fan of the heat exchanger can be effectively prevented.
When heat exchange is carried out in the air conditioner heating mode, the refrigerant is throttled and then shunted to enter the supercooling heat exchange section, so that the refrigerant enters the heat exchanger to exchange heat, the flow speed and the pressure drop of the gaseous refrigerant are reduced when the gaseous refrigerant enters the heat exchanger, and the heating performance of the air conditioner is prevented from being influenced by frosting due to the fact that the heating low-pressure side pressure is low.
In this embodiment, the branch point and the confluence point of the heat exchange pipeline of the heat exchanger adopt the Y-shaped tee joint of uniform specification to plug into, can reduce material cost, and reduce the degree of difficulty of later-stage product maintenance.
When the external environment is in the working condition of frosting easily, because this embodiment distributes the different positions of supercooling heat transfer section to the heat exchanger, has improved the defrosting efficiency, is favorable to air conditioning unit's even defrosting, improves the efficiency when improving the heating capacity.
Example 2
The embodiment shown in fig. 5 is provided for the specific tube arrangement mode of the heat exchanger.
In this embodiment, the heat exchanger is divided into 10 heat transfer areas from top to bottom, namely, a first ordinary heat transfer area 110, a first supercooling heat transfer area 210, a second ordinary heat transfer area 120, a second supercooling heat transfer area 220, a third ordinary heat transfer area 130, a third supercooling heat transfer area 230, a fourth ordinary heat transfer area 140, a fourth supercooling heat transfer area 240, a fifth ordinary heat transfer area 150, and a fifth supercooling heat transfer area 250. Wherein, the common heat exchange area is formed by the common heat exchange section pipe arrangement, and the supercooling heat exchange area is formed by the supercooling heat exchange section pipe arrangement.
In this embodiment, the specification of the common heat exchange section of each common heat exchange zone is the same, and each common heat exchange section includes a first common heat exchange section a1 and a second common heat exchange section a2 which are connected in parallel. And the specification of the supercooling heat exchange section of each supercooling heat exchange area is the same, and only the supercooling heat exchange section B is contained. The first common heat exchange section A1 and the second common heat exchange section A2 are converged and then are connected in series with the supercooling heat exchange section B.
In this embodiment, the heat exchanger is provided with a total liquid inlet pipeline 1 and a total liquid outlet pipeline 2, a liquid outlet of the total liquid inlet pipeline 1 is connected with a liquid inlet of each common heat exchange section, a liquid inlet of the total liquid outlet pipeline 2 is connected with a liquid outlet of each supercooling heat exchange section, and a liquid outlet of the total liquid outlet pipeline 2 is connected with the throttling device.
In this embodiment, the number of the supercooling heat exchange area distributions is larger, the number of supercooling heat exchange sections in each supercooling heat exchange area is correspondingly reduced, the influence of uneven heat exchange air volume on supercooling heat exchange is further reduced, and the liquid-liquid heat exchange of each flow path of the heat exchanger is more balanced.
Example 3
The embodiment shown in fig. 6 is provided for the specific tube arrangement mode of the heat exchanger.
In this embodiment, the heat exchanger is divided into 10 heat transfer areas from top to bottom, namely, a first common heat transfer area 110, a first supercooling heat transfer area 210, a second common heat transfer area 120, a second supercooling heat transfer area 220, a third common heat transfer area 130, a third supercooling heat transfer area 230, a fourth common heat transfer area 140, a fourth supercooling heat transfer area 240, a fifth common heat transfer area 150, and a fifth supercooling heat transfer area 250. Wherein, the common heat exchange area is formed by the common heat exchange section pipe arrangement, and the supercooling heat exchange area is formed by the supercooling heat exchange section pipe arrangement.
In this embodiment, the specifications of the common heat exchange sections of each common heat exchange zone are the same, and each common heat exchange section includes a first common heat exchange section a1 and a second common heat exchange section a2 which are connected in parallel. And the specification and specification of the supercooling heat exchange section of each supercooling heat exchange area are the same, and only the supercooling heat exchange section B is contained. The first common heat exchange section A1 and the second common heat exchange section A2 are converged and then are connected in series with the supercooling heat exchange section B.
In this embodiment, the heat exchanger is provided with a total liquid inlet pipeline 1 and a total liquid outlet pipeline 2, a liquid outlet of the total liquid inlet pipeline 1 is connected with a liquid inlet of each common heat exchange section, a liquid inlet of the total liquid outlet pipeline 2 is connected with a liquid outlet of each supercooling heat exchange section, and a liquid outlet of the total liquid outlet pipeline 2 is connected with the throttling device. After the number of the arranged pipes is increased, the heat exchange capacity of the heat exchanger can be further improved.
Examples 1 and 2 propose a tube layout scheme of 2 rows of tubes, and example 3 proposes a tube layout scheme of 3 rows of tubes. Which scheme is specifically used can be determined according to factors such as heat exchange power, heat exchange area and production cost of actual needs.
In addition, the utility model also provides an air conditioner which adopts the heat exchanger described in any embodiment.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the utility model, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention.
Claims (10)
1. A heat exchanger is characterized in that a body of the heat exchanger is alternately distributed with a common heat exchange area and a supercooling heat exchange area vertical to a heat exchange wind direction;
the common heat exchange area is composed of at least one section of common heat exchange section, and the supercooling heat exchange area is composed of at least one section of supercooling heat exchange section.
2. The heat exchanger of claim 1, wherein each subcooling heat exchange zone is connected in parallel.
3. The heat exchanger of claim 1, wherein the subcooling heat exchange zone comprises a first subcooling heat exchange section and a second subcooling heat exchange section connected in parallel.
4. The heat exchanger of claim 1, wherein the common heat exchange zones are connected in parallel.
5. The heat exchanger of claim 4, wherein the common heat exchange zone comprises a first common heat exchange section and a second common heat exchange section connected in parallel.
6. The heat exchanger of claim 1, wherein each of said sub-cooled heat exchange sections is connected in series with at least one of said common heat exchange sections.
7. The heat exchanger of claim 5, wherein the heat exchanger is provided with a main liquid inlet line and a main liquid outlet line;
the liquid outlet of the main liquid inlet pipeline is connected with the common heat exchange sections of the common heat exchange areas;
a liquid inlet of the main liquid outlet pipeline is connected with the supercooling heat exchange sections of the supercooling heat exchange areas, and a liquid outlet of the main liquid outlet pipeline is connected with the throttling device;
the common heat exchange area is provided with at least one row of common heat exchange sections facing the heat exchange wind direction, and the supercooling heat exchange area is provided with at least one row of supercooling heat exchange sections facing the heat exchange wind direction.
8. The heat exchanger of claim 1 wherein the common heat exchange section layout of each common heat exchange zone is the same size or the subcooling heat exchange section layout of each subcooling heat exchange zone is the same size.
9. The heat exchanger of claim 1, wherein the heat exchange lines of the heat exchanger are connected at split and merge points by Y-tees.
10. An air conditioner characterized in that the heat exchanger according to any one of claims 1 to 9 is used.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202220528963.9U CN216953290U (en) | 2022-03-11 | 2022-03-11 | Heat exchanger and air conditioner |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202220528963.9U CN216953290U (en) | 2022-03-11 | 2022-03-11 | Heat exchanger and air conditioner |
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| CN216953290U true CN216953290U (en) | 2022-07-12 |
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| CN202220528963.9U Active CN216953290U (en) | 2022-03-11 | 2022-03-11 | Heat exchanger and air conditioner |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114459080A (en) * | 2022-03-11 | 2022-05-10 | 珠海格力电器股份有限公司 | Heat exchanger and air conditioner |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114459080A (en) * | 2022-03-11 | 2022-05-10 | 珠海格力电器股份有限公司 | Heat exchanger and air conditioner |
| CN114459080B (en) * | 2022-03-11 | 2024-09-24 | 珠海格力电器股份有限公司 | Heat exchanger and air conditioner |
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