CN212618778U - Machine in heat exchanger subassembly and air conditioning - Google Patents
Machine in heat exchanger subassembly and air conditioning Download PDFInfo
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- CN212618778U CN212618778U CN202022193898.2U CN202022193898U CN212618778U CN 212618778 U CN212618778 U CN 212618778U CN 202022193898 U CN202022193898 U CN 202022193898U CN 212618778 U CN212618778 U CN 212618778U
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Abstract
The utility model discloses a machine in heat exchanger subassembly and air conditioning, the heat exchanger subassembly includes main heat exchanger and auxiliary heat exchanger, the heat transfer flow path of heat exchanger subassembly includes first flow path and second flow path, the second flow path is including parallelly connected first branch road, the second branch road, the third branch road, fourth branch road and fifth branch road, the fourth heat exchange tube of auxiliary heat exchanger is flowed through to first flow path, first heat exchange tube is flowed through to first branch road, the part second heat exchange tube is flowed through to the second branch road, the part second heat exchange tube is flowed through to the third branch road, all the other second heat exchange tubes and part third heat exchange tubes are flowed through to the fourth branch road, all the other third heat exchange tubes are flowed through to the fifth branch road, when the heat exchanger subassembly refrigerates, the refrigerant gets into first branch road simultaneously behind the first flow path, the second branch road, the third branch road, fourth branch. The utility model discloses a heat exchanger assembly can reduce the loss of pressure of refrigerant, and the refrigerant of each branch road can abundant heat transfer, and then can improve heat exchanger assembly's efficiency.
Description
Technical Field
The utility model belongs to the technical field of the air conditioning technique and specifically relates to a machine in heat exchanger subassembly and air conditioning.
Background
In the field of indoor units of air conditioners, the promotion of the heat exchange efficiency of heat exchangers becomes an increasingly urgent topic, most of heat exchangers in the prior art cause uneven flow velocity of refrigerants due to unreasonable flow path arrangement, the pressure loss of refrigerant flowing is large, the uneven distribution of a wind field can cause bias flow and refrigerant pressure loss during refrigeration to be further increased, the heat exchangers enable uneven heat exchange of the refrigerants of all flow paths, therefore, the heat exchange of the indoor units of the air conditioners is unbalanced, and the energy efficiency of the indoor units of the air conditioners is reduced.
SUMMERY OF THE UTILITY MODEL
The utility model provides a heat exchanger assembly, heat exchanger assembly has that loss of pressure is little, the heat transfer is even, the advantage that the heat transfer efficiency is high.
The utility model provides an indoor unit of air conditioner, indoor unit of air conditioner has as above heat exchanger assembly.
According to the utility model discloses heat exchanger subassembly, including main heat exchanger and supplementary heat exchanger, main heat exchanger includes first heat exchanger, second heat exchanger and third heat exchanger, first heat exchanger, the second heat exchanger with the third heat exchanger splices in proper order, first heat exchanger has first heat exchange tube, the second heat exchanger has the second heat exchange tube, the third heat exchanger has the third heat exchange tube; the auxiliary heat exchanger is arranged on the windward side of the main heat exchanger and is provided with a fourth heat exchange tube;
wherein the heat exchange flow path of the heat exchanger assembly comprises a first flow path and a second flow path, the second flow path comprises a first branch, a second branch, a third branch, a fourth branch and a fifth branch which are connected in parallel, when the heat exchanger assembly is used for refrigerating, a refrigerant flows through the first flow path and then simultaneously enters the first branch, the second branch, the third branch, the fourth branch and the fifth branch, the first flow path flows through the fourth heat exchange tube of the auxiliary heat exchanger, the first branch flows through the first heat exchange tube of the first heat exchanger, the second branch flows through a part of the second heat exchange tubes of the second heat exchanger, the third branch flows through the other part of the second heat exchange tubes of the second heat exchanger, and the fourth branch flows through the other second heat exchange tubes of the second heat exchanger and a part of the third heat exchange tubes of the third heat exchanger, the fifth branch flows through the rest of the third heat exchange tubes of the third heat exchanger.
According to the utility model discloses heat exchanger assembly, the refrigerant flows through and gets into first branch road simultaneously behind the first flow path, the second branch road, the third branch road, fourth branch road and fifth branch road, can shorten the flow path of refrigerant at each branch road from this, and then, can reduce the loss of pressure of refrigerant, improve refrigerant cold volume or thermal utilization ratio, the refrigerant flows at first branch road, the second branch road, the third branch road respectively, fourth branch road and fifth branch road can make the refrigerant of each branch road can fully exchange heat, thereby improve heat exchanger assembly's efficiency.
In some embodiments, the auxiliary heat exchanger is located on the windward side of the second heat exchanger.
In some embodiments, at least a portion of the second branch is located on a side of the third branch proximate to the first heat exchanger.
In some embodiments, the second branch comprises a greater number of the second heat exchange tubes than the third branch.
In some embodiments, the second heat exchange tube included in the fourth branch is located on a side of the third branch adjacent to the third heat exchanger.
In some embodiments, at least a portion of the fifth branch is located on a side of the fourth branch distal from the second heat exchanger.
In some embodiments, the fifth branch comprises a greater number of the third heat exchange tubes than the fourth branch comprises a total number of the third heat exchange tubes and the second heat exchange tubes.
In some embodiments, the number of the first heat exchange tubes included in the first branch is greater than the number of the second heat exchange tubes included in the second branch.
In some embodiments, the fourth heat exchange tube has an inner diameter greater than the inner diameters of the first, second, and third heat exchange tubes.
In some embodiments, the fourth heat exchange tube has a tube inner sectional area that is 1.44 times or more the tube inner sectional area of the first, second, and third heat exchange tubes.
In some embodiments, the fourth heat exchange tube has a tube inner sectional area that is 1.96 times or more the tube inner sectional area of the first, second, and third heat exchange tubes.
In some embodiments, the first flow path and the first, second, third, fourth, and fifth legs are connected by a distributor.
In some embodiments, the first heat exchanger has at least three rows of the first heat exchange tubes in the direction of gas flow, and/or the second heat exchanger has at least three rows of the second heat exchange tubes in the direction of gas flow, and/or the third heat exchanger has at least three rows of the third heat exchange tubes in the direction of gas flow.
In some embodiments, the number of heat exchange tubes of the main heat exchanger is 30 or more.
According to the embodiment of the utility model, the air-conditioning indoor unit comprises a shell, a wind wheel and a heat exchanger component, wherein the shell is provided with an air inlet and an air outlet, and the wind wheel is arranged in the shell to drive the air flow to flow from the air inlet to the air outlet; the first heat exchanger, the second heat exchanger and the third heat exchanger are all arranged in the shell and are all located on the air inlet side of the wind wheel, and the connecting portion of the second heat exchanger and the third heat exchanger is the portion, closest to the air inlet, of the main heat exchanger.
According to the utility model discloses machine in air conditioning, the refrigerant flows through and gets into first branch road simultaneously behind the first flow path, the second branch road, the third branch road, fourth branch road and fifth branch road, can shorten the flow path of refrigerant at each branch road from this, and then, can reduce the loss of pressure of refrigerant, improve refrigerant cold volume or thermal utilization ratio, the refrigerant flows at first branch road, the second branch road, the third branch road respectively, fourth branch road and fifth branch road can make the refrigerant of each branch road can fully exchange heat, thereby improve heat exchanger assembly's efficiency.
In some embodiments, the air intake is provided at an upper side of the housing, and the second heat exchanger and the third heat exchanger are formed in a substantially inverted V shape covering the wind wheel from above in a side view.
In some embodiments, the first heat exchanger, the second heat exchanger and the third heat exchanger at least partially surround the wind wheel, the first heat exchanger is disposed in front of and below the wind wheel, the second heat exchanger is disposed in front of and above the wind wheel and located between the first heat exchanger and the air inlet, an upper end of the second heat exchanger is inclined towards the rear, a lower end of the second heat exchanger is connected with an upper end of the first heat exchanger, the third heat exchanger is disposed in rear and above the wind wheel, and an upper end of the third heat exchanger is inclined towards the front and connected with an upper end of the second heat exchanger.
Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.
Drawings
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
fig. 1 is a schematic view of a partial structure of an indoor unit of an air conditioner according to an embodiment of the present invention;
fig. 2 is a schematic structural view of the heat exchanger assembly according to fig. 1.
Reference numerals:
an indoor unit 1000 of an air conditioner, a heat exchanger assembly 100,
the main heat exchanger 1 is provided with a heat exchanger,
the first heat exchanger 11, the first heat exchange pipe 111,
a second heat exchanger 12, a second heat exchange pipe 121,
a third heat exchanger 13, a third heat exchange pipe 131,
the auxiliary heat exchanger 2, the fourth heat exchange pipe 21,
the flow rates of the first flow path 3, the second flow path 4,
a first branch 41, a second branch 42, a third branch 43, a fourth branch 44, a fifth branch 45,
the air conditioner comprises a distributor 5, a shell 200, an air inlet 201, an air outlet 202 and a wind wheel 300.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary only for the purpose of explaining the present invention, and should not be construed as limiting the present invention.
The heat exchanger assembly 100 and the indoor unit 1000 of an air conditioner according to an embodiment of the present invention will be described with reference to the accompanying drawings.
As shown in fig. 1, an air conditioner indoor unit 1000 according to an embodiment of the present invention includes a casing 200, a wind wheel 300, and a heat exchanger assembly 100. The air-conditioning indoor unit 1000 is an indoor unit of a wall-mounted split air conditioner, but may be an indoor unit or an indoor unit of another air conditioner, and is not limited thereto.
Specifically, referring to fig. 1, the housing 200 has an intake vent 201 and an exhaust vent 202, the intake vent 201 being disposed at an upper side of the housing 200, and the exhaust vent 202 being disposed at a lower side of the housing 200. Generally, the width of the housing 200 in the front-rear direction is 800mm or less, and the height of the housing 200 in the up-down direction is 295mm or less. The wind wheel 300 is disposed in the housing 200 to drive airflow from the wind inlet 201 to the wind outlet 202. The rotor 300 is a cross-flow rotor, but may be other rotors, such as an axial flow rotor.
As shown in fig. 1, according to the utility model discloses heat exchanger assembly 100, including main heat exchanger 1 and auxiliary heat exchanger 2, main heat exchanger 1 includes first heat exchanger 11, second heat exchanger 12 and third heat exchanger 13, and first heat exchanger 11, second heat exchanger 12 and third heat exchanger 13 are all established in casing 200 and are all located the air inlet side of wind wheel 300, can make the air current lie in heat exchanger assembly 100 heat transfer back again by the drive of wind wheel 300 and send out indoor set 1000 of air conditioner for the heat transfer efficiency of indoor set 1000 of air conditioner is better.
The first heat exchanger 11, the second heat exchanger 12 and the third heat exchanger 13 are spliced in sequence and at least partially surround the wind wheel 300. Specifically, the first heat exchanger 11 is disposed in front of and below the wind wheel 300. Here, in the installed state of the air-conditioning indoor unit 1000, the side away from the wall is the front, the side close to the wall is the rear, the side close to the ceiling is the upper, and the side away from the ceiling is the lower. The second heat exchanger 12 is arranged above and in front of the wind wheel 300 and between the first heat exchanger 11 and the air inlet 201. The upper end of the second heat exchanger 12 is inclined rearward, and the lower end is connected to the upper end of the first heat exchanger 11. The third heat exchanger 13 is disposed at the rear upper side of the wind wheel 300, and the upper end thereof is inclined toward the front and is connected to the upper end of the second heat exchanger 12.
The second heat exchanger 12 and the third heat exchanger 13 are formed in a substantially inverted V shape covering the wind wheel 300 from above in a side view. The connection portion of the second heat exchanger 12 and the third heat exchanger 13 is a portion of the main heat exchanger 1 closest to the air intake 201, and specifically, the distance between the connection portion of the second heat exchanger 12 and the third heat exchanger 13 and the air intake 201 is shorter than the distance between any other portion of the main heat exchanger 1 and the air intake 201.
As shown in fig. 2, the first heat exchanger 11 has a first heat exchanging pipe 111, the second heat exchanger 12 has a second heat exchanging pipe 121, and the third heat exchanger 13 has a third heat exchanging pipe 131; the auxiliary heat exchanger 2 is arranged on the windward side of the main heat exchanger 1, the heat exchange capacity of the heat exchanger assembly 100 can be increased, and the auxiliary heat exchanger 2 is provided with a fourth heat exchange tube 21; it should be noted that the first heat exchange tube 111 may provide a circulation channel for the refrigerant, so that the refrigerant may smoothly flow in the circulation channel, and similarly, the second heat exchange tube 121, the third heat exchange tube 131 and the fourth heat exchange tube 21 may all provide a circulation channel for the refrigerant.
Referring to fig. 2, the heat exchange flow path of the heat exchanger assembly 100 includes a first flow path 3 and a second flow path 4, the second flow path 4 includes a first branch 41, a second branch 42, a third branch 43, a fourth branch 44 and a fifth branch 45 which are connected in parallel, when the heat exchanger assembly 100 is used for refrigerating, a refrigerant flows through the first flow path 3 and then simultaneously enters the first branch 41, the second branch 42, the third branch 43, the fourth branch 44 and the fifth branch 45, the first flow path 3 flows through the fourth heat exchange tube 21 of the auxiliary heat exchanger 2, the first branch 41 flows through the first heat exchange tube 111 of the first heat exchanger 11, the second branch 42 flows through a part of the second heat exchange tubes 121 of the second heat exchanger 12, the third branch 43 flows through another part of the second heat exchange tubes 121 of the second heat exchanger 12, the fourth branch 44 flows through the rest of the second heat exchange tubes 121 of the second heat exchanger 12 and a part of the third heat exchange tubes 131 of the third heat exchanger 13, the fifth branch 45 flows through the remaining third heat exchange tubes 131 of the third heat exchanger 13.
It can be understood that, during refrigeration, the refrigerant flows to the auxiliary heat exchanger 2, exchanges heat through the first flow path 3, flows from the first flow path 3 to the second flow path 4, that is, flows to the first branch 41, the second branch 42, the third branch 43, the fourth branch 44 and the fifth branch 45, and flows out of the main heat exchanger 1 after exchanging heat through the first branch 41, the second branch 42, the third branch 43, the fourth branch 44 and the fifth branch 45, so that the auxiliary heat exchanger 2 can enhance the heat exchange capability of the heat exchanger assembly 100.
During heating, the refrigerant flows to the main heat exchanger 1, exchanges heat through the second flow path 4, and flows from the second flow path 4 to the first flow path 3, that is, the refrigerant flows to the first flow path 3 from the first branch 41, the second branch 42, the third branch 43, the fourth branch 44, and the fifth branch 45, respectively, and flows out of the auxiliary heat exchanger 2 after exchanging heat in the first flow path 3, it should be noted that the temperature of the refrigerant decreases after exchanging heat in the first branch 41, the second branch 42, the third branch 43, the fourth branch 44, and the fifth branch 45, and the temperature further decreases after entering the second flow path 4, and therefore, energy consumption for subsequently cooling the refrigerant can be saved, and the heating performance of the heat exchanger assembly 100 can also be improved.
After flowing through the first flow path 3, the refrigerant simultaneously enters the first branch 41, the second branch 42, the third branch 43, the fourth branch 44, and the fifth branch 45. Compare with the heat exchanger that is less than five branches, the utility model discloses heat exchanger assembly 100 can shorten the refrigerant at the flow path of each branch road, from this, can reduce the loss of pressure of refrigerant, improves refrigerant cold volume or thermal utilization ratio, and the refrigerant flows at first branch road 41, second branch road 42, third branch road 43, fourth branch road 44 and fifth branch road 45 respectively and makes the refrigerant of each branch road can abundant heat transfer to improve heat exchanger assembly 100's efficiency.
As shown in table 1, for example, when the second flow path 4 is divided into four branches and five branches in different types, the influence of the refrigerant flowing through the second flow path 4 on the energy efficiency APF (Annual Performance Factor). Obviously, in the same model, when the second flow path 4 is divided into five branches, the larger the APF value is, the better the heat exchange energy efficiency is.
TABLE 1
| Number of branches of the second flow path | Model type | APF |
| 4 | 5.6KW | 5.22 |
| 4 | 6.3KW | 4.92 |
| 5 | 5.6KW | 5.47 |
| 5 | 6.3KW | 5.22 |
In one example as shown in fig. 1-2, the auxiliary heat exchanger 2 may be located on the windward side of the second heat exchanger 12. During cooling, the refrigerant flows into the auxiliary heat exchanger 2, exchanges heat through the first flow path 3, flows from the first flow path 3 to the second flow path 4, namely flows to the first branch 41, the second branch 42, the third branch 43, the fourth branch 44 and the fifth branch 45 respectively, and flows out of the main heat exchanger 1 after exchanging heat through the first branch 41, the second branch 42, the third branch 43, the fourth branch 44 and the fifth branch 45, so that the length of a transition pipe in the whole heat exchanger assembly 100 can be shortened, the design of the flow path can be further simplified, and the pressure loss of the refrigerant flowing can be reduced. According to the arrangement of the wind field, the air flow near the air inlet 201 flows faster, and the air flow is relatively slower at the position far away from the air inlet 201, and when the temperature difference between the refrigerant and the air flow at the position where the air flow flows faster is larger than that at the position where the air flow flows slower, the heat exchange efficiency of the heat exchanger assembly 100 is better. Therefore, following the flow from the portion of the heat exchanger assembly 100 close to the air intake 201 to the portion of the heat exchanger assembly 100 far from the air intake 201, the provision of the auxiliary heat exchanger 2 on the windward side of the second heat exchanger 12 enables the heat exchange efficiency of the heat exchanger assembly 100 to be better.
In another example, not shown in the drawings, the auxiliary heat exchanger 2 may also be located on the windward side of the third heat exchanger 13. During cooling, the refrigerant flows into the auxiliary heat exchanger 2, exchanges heat through the first flow path 3, flows from the first flow path 3 to the second flow path 4, namely flows to the first branch 41, the second branch 42, the third branch 43, the fourth branch 44 and the fifth branch 45 respectively, and flows out of the main heat exchanger 1 after exchanging heat through the first branch 41, the second branch 42, the third branch 43, the fourth branch 44 and the fifth branch 45, so that the length of a transition pipe in the whole heat exchanger assembly 100 can be shortened, the design of the flow path can be further simplified, and the pressure loss of the refrigerant flowing can be reduced. According to the arrangement of the wind field, the air flow near the air inlet 201 flows faster, and the air flow is relatively slower at the position far away from the air inlet 201, and when the temperature difference between the refrigerant and the air flow at the position where the air flow flows faster is larger than that at the position where the air flow flows slower, the heat exchange efficiency of the heat exchanger assembly 100 is better. Therefore, following the flow from the portion of the heat exchanger assembly 100 close to the air intake 201 to the portion of the heat exchanger assembly 100 far from the air intake 201, the provision of the auxiliary heat exchanger 2 on the windward side of the third heat exchanger 13 enables the heat exchange efficiency of the heat exchanger assembly 100 to be better.
The windward side of the auxiliary heat exchanger 2 on the second heat exchanger 12 and the windward side of the auxiliary heat exchanger 2 on the third heat exchanger 13 are only two realizable embodiments of the present invention, however, the arrangement of the auxiliary heat exchanger 2 is not limited thereto, the auxiliary heat exchanger 2 can also be arranged on the windward side between the second heat exchanger 12 and the third heat exchanger 13, the arrangement of the auxiliary heat exchanger 2 can follow the principle that the part of the heat exchanger assembly 100 close to the air inlet 201 flows to the part of the heat exchanger assembly 100 far away from the air inlet 201, and there is no limitation on the position of the auxiliary heat exchanger 2.
With reference to fig. 2, according to some embodiments of the present invention, at least part of the second branch 42 is located on a side of the third branch 43 close to the first heat exchanger 11. It can be understood that the second branch 42 flows through a part of the second heat exchange tubes 121 of the second heat exchanger 12, and the third branch 43 flows through a part of the second heat exchange tubes 121 of the second heat exchanger 12, so that at least two independent refrigerant circulation branches of the second branch 42 and the third branch 43 can be provided on the second heat exchanger 12, thereby shortening the flow path of the refrigerant on the second heat exchanger 12 and reducing the pressure loss of the refrigerant flow, and at least a part of the second branch 42 is located on a side of the third branch 43 close to the first heat exchanger 11 so that the flow path on the second heat exchanger 12 can be arranged along the first direction (e.g., the direction F1 shown in fig. 2), on one hand, the flow path on the second heat exchanger 12 can be closer to the air flow direction, on the other hand, the spatial arrangement of the heat exchanger assembly 100 is facilitated, so that the heat exchanger assembly 100 has a compact structure and occupies a.
Further, as shown in fig. 2, the second branch path 42 includes a greater number of second heat exchange tubes 121 than the third branch path 43 includes. According to the arrangement of the wind field, the airflow flows faster near the wind inlet 201, and the airflow flows relatively slower at the position far away from the wind inlet 201, and referring to fig. 1, the third branch 43 is located at the side of the second heat exchanger 12 near the wind inlet 201, and the second branch 42 is located at the side of the second heat exchanger 12 far away from the wind inlet 201, so that the wind speed of the third branch 43 is greater than that of the second branch 42.
According to a heat exchange relation formula Q ═ KA Δ t, wherein Q is a heat conduction rate, K is a heat exchange coefficient, A is a heat exchange area, and Δ t is a heat exchange average temperature difference, in the product design, Q and Δ t are preset values, K is positively correlated with the wind speed, and in order to keep balance of the heat exchange relation formula, the larger the K value is, the smaller the A value is; the smaller the K value, the larger the A value. Because the wind speed of the third branch 43 is greater than the wind speed of the second branch 42, and the heat exchange coefficient K of the third branch 43 is greater than the heat exchange coefficient K of the second branch 42, the heat exchange area a of the third branch 43 needs to be smaller than the heat exchange area a of the second branch 42 in order to keep the heat exchange of the refrigerant of the second branch 42 and the third branch 43 uniform.
The more the heat exchange tubes of the second branch 42, the larger the heat exchange area a of the second branch 42 is, the fewer the heat exchange tubes of the second branch 42 are, and the smaller the heat exchange area a of the second branch 42 is; the more the heat exchange tubes of the third branch 43, the larger the heat exchange area a of the third branch 43, the less the heat exchange tubes of the third branch 43, and the smaller the heat exchange area a of the third branch 43. Therefore, the number of the second heat exchange tubes 121 included in the second branch 42 is greater than the number of the second heat exchange tubes 121 included in the third branch 43, so that the heat exchange area a of the second branch 42 is greater than the heat exchange area a of the third branch 43, and the refrigerant heat exchange of the second branch 42 and the refrigerant heat exchange of the third branch 43 are uniform.
In some embodiments of the present invention, as shown in fig. 2, the fourth branch 44 comprises a second heat exchanging pipe 121 located on one side of the third branch 43 close to the third heat exchanger 13. It can be understood that the fourth branch 44 flows through a part of the second heat exchange tubes 121 of the second heat exchanger 12, the third branch 43 flows through a part of the second heat exchange tubes 121 of the second heat exchanger 12, and thus, at least two independent refrigerant flowing branches of the fourth branch 44 and the third branch 43 can be provided on the second heat exchanger 12, so that the flow path of the refrigerant on the second heat exchanger 12 can be shortened, and the pressure loss of the refrigerant flowing can be reduced, and the second heat exchange tube 121 included in the fourth branch 44 is located on the side of the second heat exchange tube 121 included in the third branch 43, which is far from the first heat exchanger 11, so that the flow path on the second heat exchanger 12 can be arranged along the first direction (such as the direction F1 shown in fig. 2), on one hand, the flow path on the second heat exchanger 12 can be closer to the flow direction of the air flow, on the other hand, the spatial structure layout of the heat exchanger assembly, the occupied space is saved.
With reference to fig. 2, according to some embodiments of the present invention, at least part of the fifth branch 45 is located on a side of the fourth branch 44 remote from the second heat exchanger 12. It can be understood that the fourth branch 44 flows through a part of the second heat exchange tubes 121 of the second heat exchanger 12 and a part of the third heat exchange tubes 131 of the third heat exchanger 13, and the fifth branch 45 flows into the remaining third heat exchange tubes 131 of the third heat exchanger 13, so that at least two independent refrigerant circulation branches of the fourth branch 44 and the fifth branch 45 can be provided on the third heat exchanger 13, thereby shortening the flow path of the refrigerant on the third heat exchanger 13 and reducing the pressure loss of the refrigerant flow, and at least a part of the fifth branch 45 is located on the side of the fourth branch 44 away from the second heat exchanger 12 so that the flow path on the third heat exchanger 13 can be arranged along the second direction (such as the direction F2 shown in fig. 2), on one hand, the flow path on the third heat exchanger 13 can be closer to the air flow direction, on the other hand, the spatial structure layout of the heat exchanger assembly 100 is facilitated, so that the heat exchanger assembly 100 is compact, the occupied space is saved.
In some embodiments of the present invention, as shown in fig. 2, the number of the third heat exchanging pipes 131 contained in the fifth branch 45 is greater than the total number of the third heat exchanging pipes 131 and the second heat exchanging pipes 121 contained in the fourth branch 44. According to the arrangement of the wind field, the airflow flows faster near the air inlet 201, and relatively slower at the position far away from the air inlet 201, and referring to fig. 1, the fourth branch 44 is located at the side of the third heat exchanger 13 close to the air inlet 201, and the fifth branch 45 is located at the side of the third heat exchanger 13 far away from the air inlet 201, so that the wind speed of the fourth branch 44 is greater than that of the fifth branch 45.
According to a heat exchange relation formula Q ═ KA Δ t, wherein Q is a heat conduction rate, K is a heat exchange coefficient, A is a heat exchange area, and Δ t is a heat exchange average temperature difference, in the product design, Q and Δ t are preset values, K is positively correlated with the wind speed, and in order to keep balance of the heat exchange relation formula, the larger the K value is, the smaller the A value is; the smaller the K value, the larger the A value. Because the wind speed of the fourth branch 44 is greater than the wind speed of the fifth branch 45, and the heat exchange coefficient K of the fourth branch 44 is greater than the heat exchange coefficient K of the fifth branch 45, the heat exchange area a of the fourth branch 44 is required to be smaller than the heat exchange area a of the fifth branch 45 in order to maintain uniform heat exchange between the refrigerant of the fourth branch 44 and the refrigerant of the fifth branch 45.
The more the heat exchange tubes of the fourth branch 44, the larger the heat exchange area a of the fourth branch 44 is, the fewer the heat exchange tubes of the fourth branch 44 are, and the smaller the heat exchange area a of the fourth branch 44 is; the more the heat exchange tubes of the fifth branch 45, the larger the heat exchange area a of the fifth branch 45, the less the heat exchange tubes of the fifth branch 45, and the smaller the heat exchange area a of the fifth branch 45. Therefore, the number of the third heat exchange tubes 131 included in the fifth branch 45 is greater than the total number of the third heat exchange tubes 131 and the second heat exchange tubes 121 included in the fourth branch 44, so that the heat exchange area a of the fifth branch 45 is greater than the heat exchange area a of the fourth branch 44, and the refrigerant heat exchange of the fourth branch 44 and the fifth branch 45 is uniform.
In some embodiments of the utility model, as shown in fig. 2, the quantity of the first heat exchange tube 111 that first branch 41 contains is more than the quantity of the second heat exchange tube 121 that second branch 42 contains, and in the same way, the branch wind speed that is closer to air intake 201 is bigger, therefore, the wind speed of second branch 42 is greater than the wind speed of first branch 41, according to heat transfer relational expression Q ═ KA Δ t, for keeping the refrigerant heat transfer of first branch 41 and second branch 42 even, it is less than the heat transfer area a of first branch 41 to need the heat transfer area a of second branch 42, and then, the quantity of the first heat exchange tube 111 that first branch 41 contains is more than the quantity of the second heat exchange tube 121 that second branch 42 contains, can make the heat transfer area a of first branch 41 be greater than the heat transfer area a of second branch 42, thereby make the refrigerant heat transfer of first branch 41 and second branch 42 even.
According to some embodiments of the present invention, the inner diameter of the fourth heat exchange tube 21 is larger than the inner diameters of the first heat exchange tube 111, the second heat exchange tube 121 and the third heat exchange tube 131. As shown in fig. 1, along the air flow direction, the windward side of the main heat exchanger 1, that is, the upstream of the main heat exchanger 1, adopts the heat exchange tube with small pipe diameter to reduce the material consumption of the heat exchange tube, and then the overall cost of the heat exchanger assembly 100 is significantly reduced, but when the refrigerant passes through the heat exchange tube with small pipe diameter, the heat exchange resistance is large, the pressure loss is large, and the refrigerant circulation is not facilitated. The cost of the heat exchanger assembly 100 and the refrigerant circulation flow efficiency are comprehensively considered, the auxiliary heat exchanger 2 is arranged on the windward side of the main heat exchanger 1, and the diameter of the fourth heat exchange tube 21 is larger than the diameters of the first heat exchange tube 111, the second heat exchange tube 121 and the third heat exchange tube 131, so that the heat exchange efficiency of the heat exchanger assembly 100 is good while the production cost of the heat exchanger assembly 100 is reduced.
In some embodiments of the present invention, the tube inner sectional area of the fourth heat exchange tube 21 is more than 1.44 times of the tube inner sectional area of the first heat exchange tube 111, the second heat exchange tube 121 and the third heat exchange tube 131, the tube inner sectional area can be understood as the cross-sectional area of the heat exchange tube calculated by taking the inner diameter of the heat exchange tube as the standard, for example, the inner diameter of the fourth heat exchange tube 21 can be 6mm, and the tube inner sectional area of the fourth heat exchange tube 21 is 9 pi mm2The inner diameters of the first heat exchange tube 111, the second heat exchange tube 121 and the third heat exchange tube 131 may be all 5mm, and the tube inner sectional areas of the first heat exchange tube 111, the second heat exchange tube 121 and the third heat exchange tube 131 are all 6.25 pi mm2Thus, 9 π/6.25 π is 1.44. Since the first flow path 3 flows through the fourth heat exchange tube 21, the five branches of the second flow path 4 flow through the first heat exchange tube 111, the second heat exchange tube 121 and the third heat exchange tube 131, and the tube inner sectional area of the fourth heat exchange tube 21 is more than 1.44 times of the tube inner sectional area of the first heat exchange tube 111, the second heat exchange tube 121 and the third heat exchange tube 131, the first flow path 3 can rapidly disperse the refrigerant to the five branches of the first flow path 4, or the refrigerant is rapidly converged to the first flow path 3 from the five branches of the first flow path 4, the refrigerant flowing efficiency can be improved, and the heat exchange effect of the air conditioner 1000 is further improved.
Go toIncidentally, the fourth heat exchange tube 21 has a tube inner sectional area 1.96 times or more the tube inner sectional areas of the first, second and third heat exchange tubes 111, 121 and 131, for example, the inner diameter of the fourth heat exchange tube 21 may be 7mm, and the tube inner sectional area of the fourth heat exchange tube 21 is 12.25 pi mm2The inner diameters of the first heat exchange tube 111, the second heat exchange tube 121 and the third heat exchange tube 131 may be all 5mm, and the tube inner sectional areas of the first heat exchange tube 111, the second heat exchange tube 121 and the third heat exchange tube 131 are all 6.25 pi mm2Thus, 12.25 π/6.25 π is 1.96. Therefore, the tube internal sectional area of the fourth heat exchange tube 21 is larger than that of the first heat exchange tube 111, the second heat exchange tube 121 and the third heat exchange tube 131, so that more refrigerants can flow in the fourth heat exchange tube 21, the first flow path 3 can rapidly disperse the refrigerants to five branch paths of the first flow path 4, or the refrigerants are rapidly converged to the first flow path 3 from five branch paths of the first flow path 4, the flowing efficiency of the refrigerants can be improved, and the heat exchange effect of the air conditioner 1000 is improved.
As shown in fig. 2, according to some embodiments of the present invention, the first flow path 3 and the first, second, third, fourth and fifth branches 41, 42, 43, 44, 45 are connected by the distributor 5. Therefore, the distributor 5 can conveniently converge the refrigerant in the first flow channel 3 to the distributor 5 and then respectively flow to the first branch 41, the second branch 42, the third branch 43, the fourth branch 44 and the fifth branch 45; the refrigerant in the first branch passage 41, the second branch passage 42, the third branch passage 43, the fourth branch passage 44 and the fifth branch passage 45 is collected in the distributor 5 and then flows to the first flow passage 3.
In some embodiments of the present invention, referring to fig. 2, the first heat exchanger 11 has at least three rows of first heat exchange tubes 111 in the airflow flowing direction, and/or the second heat exchanger 12 has at least three rows of second heat exchange tubes 121 in the airflow flowing direction, and/or the third heat exchanger 13 has at least three rows of third heat exchange tubes 131 in the airflow flowing direction. Therefore, the insufficient heat exchange caused by too few rows of heat exchange tubes can be avoided, and the waste caused by too many heat exchange tubes can be prevented.
According to some embodiments of the present invention, referring to fig. 2, the number of heat exchange tubes of the main heat exchanger 1 is more than 30. This enables the heat exchanger assembly 100 to be more energy efficient for heat exchange.
Further, taking the number of the heat exchange tubes of the main heat exchanger 1 as 30 for example, the first branch 41 includes 7 first heat exchange tubes 111, the second branch 42 includes 7 second heat exchange tubes 121, the third branch 43 includes 5 second heat exchange tubes 121, the fourth branch 44 includes 1 second heat exchange tube 121 and 4 third heat exchange tubes 131, and the fifth branch 45 includes 6 third heat exchange tubes 131, as shown in table 2, the number of the five branch heat exchange tubes is allocated with different influences on energy efficiency APF, which is called Annual Performance Factor, i.e. Annual energy consumption rate). As can be seen from the table 2, the utility model discloses a heat transfer efficiency is better.
TABLE 2
In some embodiments of the present invention, the width of the casing 200 in the front-back direction is less than 800mm, and the height of the casing 200 in the up-down direction is less than 295mm, so that the size of the air conditioner indoor unit 1000 is more suitable, and the overall size of the air conditioner indoor unit 1000 is reduced.
In the description of the present invention, it is to be understood that the terms "center", "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, indicate the orientation or positional relationship indicated based on the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be construed as limiting the present invention. Furthermore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an illustrative embodiment," "an example," "a specific example," or "some examples" or the like 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 present invention. In this specification, the schematic representations of the terms used above do not necessarily 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.
While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.
Claims (17)
1. A heat exchanger assembly, comprising:
the main heat exchanger comprises a first heat exchanger, a second heat exchanger and a third heat exchanger, the first heat exchanger, the second heat exchanger and the third heat exchanger are sequentially spliced, the first heat exchanger is provided with a first heat exchange tube, the second heat exchanger is provided with a second heat exchange tube, and the third heat exchanger is provided with a third heat exchange tube;
the auxiliary heat exchanger is arranged on the windward side of the main heat exchanger and is provided with a fourth heat exchange tube;
wherein the heat exchange flow path of the heat exchanger assembly comprises a first flow path and a second flow path, the second flow path comprises a first branch, a second branch, a third branch, a fourth branch and a fifth branch which are connected in parallel,
when the heat exchanger assembly is used for refrigerating, refrigerant flows through the first flow path and then respectively enters the first branch path, the second branch path, the third branch path, the fourth branch path and the fifth branch path,
the first flow path flows through the fourth heat exchange tube of the auxiliary heat exchanger, the first branch path flows through the first heat exchange tube of the first heat exchanger, the second branch path flows through a part of the second heat exchange tube of the second heat exchanger, the third branch path flows through the second heat exchange tube of the other part of the second heat exchanger, the fourth branch path flows through the rest of the second heat exchange tubes of the second heat exchanger and a part of the third heat exchange tubes of the third heat exchanger, and the fifth branch path flows through the rest of the third heat exchange tubes of the third heat exchanger.
2. The heat exchanger assembly of claim 1, wherein the auxiliary heat exchanger is located on a windward side of the second heat exchanger.
3. The heat exchanger assembly of claim 1, wherein at least a portion of the second leg is located on a side of the third leg adjacent to the first heat exchanger.
4. The heat exchanger assembly of claim 3, wherein the second leg comprises a greater number of the second heat exchange tubes than the third leg comprises.
5. The heat exchanger assembly of claim 1, wherein the second heat exchange tube of the fourth circuit branch is located on a side of the third circuit branch adjacent the third heat exchanger.
6. The heat exchanger assembly of claim 1, wherein at least a portion of the fifth branch is located on a side of the fourth branch distal from the second heat exchanger.
7. The heat exchanger assembly of claim 6, wherein the fifth circuit comprises a greater number of the third heat exchange tubes than the fourth circuit comprises a total number of the third heat exchange tubes and the second heat exchange tubes.
8. The heat exchanger assembly of claim 1, wherein the first circuit comprises a number of the first heat exchange tubes equal to or greater than a number of the second heat exchange tubes of the second circuit.
9. The heat exchanger assembly of claim 1, wherein the fourth heat exchange tube has an inner diameter greater than the inner diameters of the first, second and third heat exchange tubes.
10. The heat exchanger assembly of claim 9, wherein the fourth heat exchange tube has a tube inner cross-sectional area that is greater than 1.44 times the tube inner cross-sectional area of the first, second and third heat exchange tubes.
11. The heat exchanger assembly of claim 10, wherein the fourth heat exchange tube has a tube inner cross-sectional area that is greater than 1.96 times the tube inner cross-sectional area of the first, second and third heat exchange tubes.
12. The heat exchanger assembly of claim 1, wherein the first flow path and the first, second, third, fourth, and fifth legs are connected by a distributor.
13. The heat exchanger assembly of claim 1, wherein the first heat exchanger has at least three rows of the first heat exchange tubes in a direction of airflow,
and/or the second heat exchanger is provided with at least three rows of second heat exchange tubes in the airflow flowing direction,
and/or the third heat exchanger is provided with at least three rows of third heat exchange tubes in the airflow flowing direction.
14. The heat exchanger assembly according to claim 1, wherein the number of heat exchange tubes of the main heat exchanger is 30 or more.
15. An indoor unit of an air conditioner, comprising:
a housing having an air inlet and an air outlet;
the wind wheel is arranged in the shell to drive airflow to flow from the air inlet to the air outlet;
the heat exchanger assembly according to any one of claims 1 to 14, wherein the first heat exchanger, the second heat exchanger and the third heat exchanger are all arranged in the housing and are all located on an air inlet side of the wind wheel, and a connection portion of the second heat exchanger and the third heat exchanger is a portion of the main heat exchanger closest to the air inlet.
16. An indoor unit of an air conditioner according to claim 15, wherein the air inlet is provided at an upper side of the casing,
the second heat exchanger and the third heat exchanger are formed in a substantially inverted V shape covering the wind wheel from above in a side view.
17. An indoor unit of an air conditioner according to claim 16, wherein the first heat exchanger, the second heat exchanger and the third heat exchanger at least partially surround the wind wheel, the first heat exchanger is disposed in front of and below the wind wheel, the second heat exchanger is disposed in front of and above the wind wheel and is located between the first heat exchanger and the air inlet, an upper end of the second heat exchanger is inclined rearward, a lower end of the second heat exchanger is connected to an upper end of the first heat exchanger, the third heat exchanger is disposed behind and above the wind wheel, and an upper end of the third heat exchanger is inclined forward and is connected to an upper end of the second heat exchanger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022193898.2U CN212618778U (en) | 2020-09-29 | 2020-09-29 | Machine in heat exchanger subassembly and air conditioning |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022193898.2U CN212618778U (en) | 2020-09-29 | 2020-09-29 | Machine in heat exchanger subassembly and air conditioning |
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| Publication Number | Publication Date |
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| CN212618778U true CN212618778U (en) | 2021-02-26 |
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| CN202022193898.2U Active CN212618778U (en) | 2020-09-29 | 2020-09-29 | Machine in heat exchanger subassembly and air conditioning |
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