WO2020047927A1 - 换热器组件和空调室内机 - Google Patents

换热器组件和空调室内机 Download PDF

Info

Publication number
WO2020047927A1
WO2020047927A1 PCT/CN2018/108820 CN2018108820W WO2020047927A1 WO 2020047927 A1 WO2020047927 A1 WO 2020047927A1 CN 2018108820 W CN2018108820 W CN 2018108820W WO 2020047927 A1 WO2020047927 A1 WO 2020047927A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
branch
flows
row
heat exchange
Prior art date
Application number
PCT/CN2018/108820
Other languages
English (en)
French (fr)
Inventor
张强
谢李高
宋分平
山崎和雄
吕建华
刘行
张晶晶
陈运强
Original Assignee
广东美的制冷设备有限公司
美的集团股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN201821443587.3U external-priority patent/CN209042727U/zh
Priority claimed from CN201811028543.9A external-priority patent/CN109269071B/zh
Priority claimed from CN201821444281.XU external-priority patent/CN209042730U/zh
Application filed by 广东美的制冷设备有限公司, 美的集团股份有限公司 filed Critical 广东美的制冷设备有限公司
Priority to JP2019546860A priority Critical patent/JP6858268B2/ja
Publication of WO2020047927A1 publication Critical patent/WO2020047927A1/zh

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers

Definitions

  • the present application relates to the technical field of air-conditioning products, and in particular, to a heat exchanger assembly and an air-conditioning indoor unit.
  • the air conditioner heat exchanger with better heat exchange performance in the exemplary technology generally includes a front heat exchanger, a middle heat exchanger, and a rear heat exchanger.
  • the three are semi-enclosed.
  • the refrigeration agent is divided into three paths by the three-way pipe, and enters the front heat exchanger, the middle heat exchanger, and the rear heat exchanger for heat exchange.
  • the front heat exchanger, the middle heat exchanger, and the rear heat exchanger are limited by The rectangular space in the air-conditioning casing, therefore, their respective sizes are also different, so that the number of heat exchange tubes that can be set in each heat exchanger is also different, and the size of the middle heat exchanger is often the front heat exchanger.
  • the number of heat exchange tubes provided in the middle heat exchanger is far more than that of the front or rear heat exchanger. In this way, the refrigerant enters the front heat exchanger. After the heat exchanger or rear heat exchanger and before it exits the air-conditioning heat exchanger, the number of heat exchange tubes that pass through will be far less than the number of heat exchanger tubes that the refrigerant enters the middle heat exchanger. In other words, the refrigerant is in the front heat exchanger or When heat is exchanged in the rear heat exchanger, it is likely that the heat is discharged from the indoor heat exchanger without sufficient heat exchange.
  • the main purpose of this application is to propose a heat exchanger assembly, which aims to improve the heat exchange balance between the middle heat exchanger, the front heat exchanger, and the rear heat exchanger of the air conditioner heat exchanger in the exemplary technology, and improve the heat exchange of the air conditioner. Energy efficiency.
  • the heat exchanger assembly proposed in this application includes:
  • the main heat exchanger is arranged in a semi-enclosed shape.
  • the main heat exchanger includes a front heat exchanger, a middle heat exchanger, and a rear heat exchanger.
  • the front heat exchanger, the middle heat exchanger, and the rear heat exchanger are in At least two rows of heat exchange tubes are provided in the air inlet direction, and the number of heat exchange tubes of the middle heat exchanger is greater than the front heat exchanger and the rear heat exchanger;
  • the back-pipe heat exchanger is installed on the windward side of the main body heat exchanger
  • the heat exchange flow path of the heat exchanger assembly is divided into a first branch, a second branch, and a third branch after passing through the back-tube heat exchanger.
  • a branch, a second branch, and a third branch flow from the heat exchange tubes on the windward side of the main heat exchanger toward the heat exchange tubes on the leeward side; the first branch flows through the front heat exchanger
  • the second branch flows through the heat exchanger tubes of the middle heat exchanger
  • the third branch flows through the heat exchanger tubes of the rear heat exchanger
  • the first branch At least one of the third branch and the third branch is also disposed across the heat exchange tubes of the middle heat exchanger.
  • the pairwise difference between the number of heat exchange tubes flowing through the first branch, the second branch, and the third branch is less than or equal to three.
  • the front heat exchanger, the middle heat exchanger, and the rear heat exchanger are each provided with two rows of heat exchange tubes, and the total number of heat exchange tubes of the main heat exchanger is 18-22.
  • the third branch flows through all the heat exchange tubes of the rear heat exchanger, the second branch flows through a part of the heat exchange tubes of the middle heat exchanger, and the first branch The remaining heat exchange tubes flowing through the middle heat exchanger and all the heat exchange tubes of the front heat exchanger.
  • the heat exchange tubes of the front heat exchanger include a first outer row and a first inner row
  • the heat exchange tubes of the middle heat exchanger include a second outer row and a second inner row.
  • the outer row and the second row are located on the windward side of the main heat exchanger;
  • the first branch flows from the second outer row, flows along the second outer row and enters the first outer row through a first crossover pipe, and flows in sequence.
  • the second branch flows in from the second outer row, and sequentially flows through the remaining of the second outer row A portion, and the entire second inner row, flows out of the second inner row.
  • the first branch flows from a heat exchange tube in the middle of the second outer row, flows along the second outer row toward one side of the front heat exchanger, and then passes through the first
  • the jumper pipe enters the heat exchange pipe of the first outer row near the middle heat exchanger, and flows through the entire first outer row and the first inner row in sequence, and then from the first inner row near the The heat exchanger tubes of the heat exchanger flow out.
  • the second branch flows from a heat exchange tube adjacent to a heat transfer tube flowing from the first branch on the second outer row, and heat is transferred along the second outer row toward the rear
  • One side of the heat exchanger flows from the second outer row into the second inner row of heat exchange tubes near the rear heat exchanger, and along the second inner row toward the front heat exchanger.
  • One side flows, and then flows out from the second inner row of heat exchange tubes near the front heat exchanger.
  • the rear heat exchanger includes a third inner row and a third outer row, and the third outer row is located on the windward side of the main heat exchanger;
  • the third branch flows from the heat exchange tubes of the third outer row close to the middle heat exchanger, and sequentially flows through the entire third outer row and the third inner row, and from the third An inner row of heat exchange tubes near the middle heat exchanger flows out.
  • the heat exchange tubes in the front heat exchanger include a first outer row and a first inner row
  • the heat exchange tubes in the middle heat exchanger include a second outer row and a second inner row
  • the heat exchange tubes in the rear heat exchanger include a third outer row and a third inner row; the first outer row, the second outer row, and the third outer row are all disposed near the windward side of the main heat exchanger;
  • the first branch flows from the first outer row, flows through the entire first outer row and the first inner row, and then enters the station through the first crossover pipe.
  • the second inner row flows out of the second inner row; the second branch flows in from the second outer row, and flows through the entire second outer row and the second inner row in sequence.
  • the remaining part flows out from the second inner row; the third branch flows from the third outer row, and flows through the entire third outer row and the third inner row in sequence, and from the third inner row Drain out
  • the first branch line flows in from the first outer row of heat exchange tubes close to the middle heat exchanger, and sequentially flows through the entire first outer row and the first inner row to reach the first row.
  • Heat exchange tubes of a first inner row close to the middle heat exchanger, and then enter the second inner row through the first crossover pipe;
  • the heat exchange tubes of the front heat exchanger include a first outer row and a first inner row
  • the heat exchange tubes of the middle heat exchanger include a second outer row and a second inner row
  • the rear exchange The heat exchanger tubes of the heat exchanger include a third outer row and a third inner row, and the first outer row, the second outer row, and the third outer row are all disposed near the windward side of the main heat exchanger;
  • the first branch flows from the second outer row, flows along the second outer row and enters the first outer row through a first crossover pipe, and flows in sequence. Enters the second inner row through the entire first outer row and the first inner row, and then flows out from the second inner row through the second crossover pipe; the second branch path is from the second outer row The inflow flows through the remainder of the second outer row and the second inner row in sequence, and flows out from the second inner row; the third branch flows in from the third outer row, and flows through in sequence The entire third outer row and the third inner row, and flow out from the third inner row;
  • the diameter of the heat exchange tube of the back-pipe heat exchanger is larger than that of the main body heat exchanger.
  • the back-tube heat exchanger is installed on the windward side of the middle heat exchanger.
  • the back-pipe heat exchanger is disposed near the front heat exchanger relative to the rear heat exchanger.
  • the number of heat exchange tubes of the back-pipe heat exchanger is 2 to 4.
  • the present application also proposes an air-conditioning indoor unit, including a heat exchanger component and a casing for accommodating the heat exchanger component.
  • the heat exchanger component includes:
  • the main heat exchanger is arranged in a semi-enclosed shape.
  • the main heat exchanger includes a front heat exchanger, a middle heat exchanger, and a rear heat exchanger.
  • the front heat exchanger, the middle heat exchanger, and the rear heat exchanger are in At least two rows of heat exchange tubes are provided in the air inlet direction, and the number of heat exchange tubes of the middle heat exchanger is greater than the front heat exchanger and the rear heat exchanger;
  • the back-pipe heat exchanger is installed on the windward side of the main body heat exchanger
  • the heat exchange flow path of the heat exchanger assembly is divided into a first branch, a second branch, and a third branch after passing through the back-tube heat exchanger.
  • a branch, a second branch, and a third branch flow from the heat exchange tubes on the windward side of the main heat exchanger toward the heat exchange tubes on the leeward side; the first branch flows through the front heat exchanger
  • the second branch flows through the heat exchanger tubes of the middle heat exchanger
  • the third branch flows through the heat exchanger tubes of the rear heat exchanger
  • the first branch At least one of the third branch and the third branch is also disposed across the heat exchange tubes of the middle heat exchanger.
  • the width dimension of the casing in the front-back direction is less than 800mm, and the height dimension of the casing in the vertical direction is less than 295mm.
  • the angle between the arrangement direction of the rear heat exchanger and the up-down direction ranges from 38 ° to 48 °.
  • an included angle between the arrangement direction of the middle heat exchanger and the front heat exchanger and the up-down direction ranges from 45 ° to 55 °.
  • the air conditioner indoor unit further includes a wind deflector, and the wind deflector bridges the middle heat exchanger and the rear heat exchanger. Between the windward sides of the devices near each other.
  • the heat exchanger assembly of the technical solution of the present application includes a main heat exchanger and a back-pipe heat exchanger provided on the windward side of the main heat exchanger.
  • the main heat exchanger includes a front heat exchanger, a middle heat exchanger, and a rear heat exchanger.
  • the heat exchange flow path after passing through the back-tube heat exchanger is divided into the first branch, the second branch, and the third branch.
  • the first branch flows through the front heat exchanger and the second branch.
  • the current flows through the middle heat exchanger, and the third branch flows through the rear heat exchanger.
  • FIG. 1 is a schematic structural diagram of an embodiment of an air-conditioning indoor unit of the present application
  • FIG. 2 is a schematic flow path diagram of a first embodiment of a heat exchanger assembly of the present application
  • FIG. 3 is a schematic flow path diagram of a second embodiment of a heat exchanger assembly of the present application.
  • FIG. 4 is a schematic flow diagram of a third embodiment of a heat exchanger assembly of the present application.
  • the directional indication is only used to explain in a specific posture (as shown in the drawings) (Shown) the relative positional relationship, movement, etc. of the various components, if the specific posture changes, the directional indicator will change accordingly.
  • This application proposes a heat exchanger assembly and an air-conditioning indoor unit having the heat exchanger assembly.
  • the heat exchanger assembly can also be applied to an air-conditioning integrated machine or an air-conditioning outdoor unit. Limited to this.
  • the air-conditioning indoor unit is a wall-mounted air-conditioning indoor unit, which specifically includes a housing 3 and a cross-flow wind wheel 4 provided in the housing 3.
  • the heat exchanger assembly 1 is also provided in the machine Inside the casing 3 and located between the air inlet on the casing 3 and the cross-flow wind wheel 4 to exchange heat for the air sucked by the cross-flow wind wheel 4.
  • the heat exchanger assembly 1 is located on the upper side of the cross-flow wind wheel 4.
  • the air conditioner indoor unit may also be a vertical indoor air conditioner or the like.
  • the heat exchanger assembly 1 includes:
  • the main heat exchanger is arranged in a semi-circle around the cross-flow wind wheel 4;
  • the main heat exchanger includes a front heat exchanger 11, a middle heat exchanger 12, and a rear heat exchanger 13, the front heat exchanger 11, the middle heat exchanger 12, and
  • the rear heat exchanger 13 is provided with at least two rows of heat exchange tubes in the air inlet direction, and the number of heat exchange tubes of the middle heat exchanger 12 is greater than that of the front heat exchanger 11 and the rear heat exchanger 13;
  • the back pipe heat exchanger 14 is installed on the windward side of the main heat exchanger
  • the front heat exchanger 11, the middle heat exchanger 12, and the rear heat exchanger 13 are provided with two rows of heat exchange tubes in the air inlet direction, which avoids too few rows of heat exchange tubes and insufficient heat exchange.
  • three or even four rows can be set up in the inlet air direction.
  • Heat pipe this design is not limited to this.
  • the heat exchange tubes of the front heat exchanger 11 include a first outer row 111 and a first inner row 112
  • the heat exchange tubes of the middle heat exchanger 12 include a second outer row 121 and a second inner row 122.
  • the heat exchange tubes of the heat exchanger 13 include a third outer row 131 and a third inner row 132.
  • the first outer row 111, the second outer row 121, and the third outer row 131 are all located on the windward side of the main heat exchanger. It is easy to understand that the addition of the back pipe heat exchanger 14 on the windward side of the main heat exchanger is also to enhance the heat exchange capacity of the heat exchanger assembly 1, without loss of generality, in order to bring the energy efficiency of the back pipe heat exchanger 14 into full play. Maximize and install it on the windward side of the middle heat exchanger 12 with the largest windward area. In particular, it should be avoided as far as possible that there is a gap between the ends of the middle heat exchanger 12 and the rear heat exchanger 13 that are close to each other.
  • the middle heat exchanger 12 and the A wind deflector 16 is also connected across the windward side of the rear heat exchanger 13; for example, but not limited to, both ends of the wind deflector 16 are attached to the middle heat exchanger 12 and the rear heat exchanger 13 by sponges, respectively.
  • the method of sponge bonding also helps users to repair or replace the heat exchanger.
  • windshield plate 16 is disassembled; of course, in other embodiments, windshield plate 16 can also be installed on middle heat exchanger 12 and rear heat exchanger 13 by means of screw locking. The design is not limited to this. this.
  • a wind deflector 16 may also be added between the two to avoid the situation of air leakage from the heat exchanger assembly 1.
  • the air conditioning heat exchange cycle system also includes outdoor heat exchangers, compressors, and the like.
  • one end of the back pipe heat exchanger 14 is connected to the main heat exchanger, and the other end is connected to the first refrigerant main pipe 24, and the first refrigerant main pipe 24 is used to connect to the outdoor heat exchanger.
  • the device 14 is divided into a first branch 21, a second branch 22, and a third branch 23 after passing through the back-tube heat exchanger 14, and the first branch 21, the second branch 22, and the third branch 23 are all The heat exchange tubes on the windward side of the main heat exchanger flow toward the heat exchange tubes on the leeward side; the first branch 21 and the second branch 22 share all the heat exchanger tubes of the front heat exchanger 11 and the middle heat exchanger 12, and At least one of the branch 21 and the second branch 22 is disposed across the heat exchange tubes of the front heat exchanger 11 and the middle heat exchanger 12, and the third branch 23 flows through all the heat exchange tubes of the rear heat exchanger 13.
  • the refrigerant sent by the compressor first enters the heat exchanger assembly 1 through the second refrigerant header 25, and flows through the first branch 21, the second branch 22, and the third branch 23 to complete the heat exchange, and is collected and combined.
  • Backing tube 14 through the heat exchanger after re-entering the outdoor heat exchanger header pipe 24 through the first refrigerant, and finally back to the compressor. It should be noted that this design is not limited to this.
  • the first branch 21 flows through all the heat exchange tubes of the front heat exchanger 11, and the second branch 22 and the third branch 23 share and exchange. All the heat exchange tubes of the heat exchanger 12 and the rear heat exchanger 13, and at least one of the second branch 22 and the third branch 23 is provided across the heat exchange tubes of the middle heat exchanger 12 and the rear heat exchanger 13.
  • the refrigerant passes through the back-pipe heat exchanger 14 and is split by a distributor 15 into the first branch 21, the second branch 22, and the third branch 23,
  • the refrigerant can also be divided by a flute tube or other structure, which is not limited in this design.
  • the first branch 21, the second branch 22, and the third branch 23 are all adopted from the outside.
  • the principle of the flow direction of the heat exchange tube (on the windward side) to the inside (leeward side) is to increase the heat exchange temperature difference and maximize the heat exchange efficiency.
  • Table 1 compares and analyzes the heat exchanger assembly 1 in the refrigeration industry. Under the circumstances, the flow path from the outer heat transfer tube to the inner heat transfer tube and other types of flow paths affect the APF (energy efficiency ratio).
  • Input tube entry method APF All three channels in the input tube enter from the outside to the inside 6.42 Two lines in the input tube enter the outside into the inside 6.25 Two lines in the input tube enter the outside into the inside 6.07
  • the size of the casing 3 limits the number of heat exchange tubes between the front heat exchanger 11 and the middle heat exchanger 12, and the refrigerant "The heat exchanger 12 exchanges heat, resulting in uneven heat exchange and low energy efficiency.”
  • the flow path design of the component 1 of the heat exchanger 12 also emphasizes that the first branch 21 and the second branch 22 are exchanged before sharing.
  • the heat exchanger tubes of the heat exchanger 11 and the middle heat exchanger 12, and at least one of the first branch circuit 21 and the second branch circuit 22 is provided as a heat exchange tube bridged between the front heat exchanger 11 and the middle heat exchanger 12.
  • the flow path is no longer limited to flow through the front heat exchanger 11 or the middle heat exchanger 12, but part of the heat exchange tubes of the two are connected in series, so that it can effectively make up for the front heat exchanger 11 Insufficient heat exchange can also avoid the structural waste of the middle heat exchanger 12, thereby effectively realizing the heat exchange balance between the front heat exchanger 11 and the middle heat exchanger 12, and the improvement of its energy efficiency.
  • the difference between the number of heat exchange tubes that each of the first branch 21 and the second branch 22 flow through is controlled to be less than or equal to 3, so as to avoid that the heat exchange efficiency difference between the two is too large and affects the front exchange.
  • the two-to-two difference between the number of heat exchange tubes flowing through the first branch 21, the second branch 22, and the third branch 23 is controlled to be less than or equal to 3, so that the front heat exchanger 11,
  • the heat exchange balance between the middle heat exchanger 12 and the rear heat exchanger 13 improves the overall energy efficiency of the heat exchanger assembly 1.
  • the width L of the cabinet 3 in the front-to-rear direction is less than 800 mm.
  • the height dimension H of the casing 3 in the up-down direction is less than 295mm; for the heat exchanger assembly 1 adapted to the size of the casing 3, the total number of heat exchange tubes in the main heat exchanger is set to 18 to 22 to limit the It is ensured that the heat exchanger assembly 1 maintains a high energy efficiency in the installation space.
  • the number of heat exchange tubes of the main heat exchanger is 20.
  • the diameter D of the cross-flow wind wheel 4 is selected between 115 mm and 125 mm, and the inner side of the main heat exchanger and the The distance S between the outer side of the airflow wheel 4 is maintained greater than 10mm, and in order to ensure that the main heat exchanger semi-circles the crossflow airflow wheel 4, it can achieve a better effect of improving the heat exchange energy efficiency and a reliable design of dew condensation.
  • the angle between the rear heat exchanger 13 and the vertical direction is between 38 ° and 48 °, and the angle between the middle heat exchanger 12 and the front heat exchanger 11 and the vertical direction is between 45 ° and 55 °.
  • the heat exchanger assembly 1 of the technical solution of the present application includes a main body heat exchanger and a back-pipe heat exchanger 14 provided on the windward side of the main body heat exchanger.
  • the main body heat exchanger includes a front heat exchanger 11, a middle heat exchanger 12, and a rear heat exchanger.
  • the heat exchange flow path 2 after passing through the back-tube heat exchanger 14 is divided into the first branch 21, the second branch 22, and the third branch 23, and the first branch
  • the circuit 21 flows through the front heat exchanger 11, the second branch 22 flows through the middle heat exchanger 12, and the third branch 23 flows through the rear heat exchanger 13.
  • the refrigerant of the heat pipe continues to pass, avoiding the possibility of the first branch 21 passing through the heat exchange tube of the front heat exchanger 11 or the third branch 23 passing only the heat exchange tube of the rear heat exchanger 13 Insufficient (because there are fewer heat exchange tubes for the front heat exchanger 11 and the rear heat exchanger 13), and the second branch 22 only passes through the heat exchange tubes of the middle heat exchanger 12 (due to the middle heat exchange Heat exchange tubes 12 more), but also makes the front heat exchanger 11, 13 after the effect of heat transfer between the heat exchanger 12 and the heat exchanger in a more balanced, effectively increasing the energy efficiency of the heat exchanger assembly.
  • the use of small-diameter heat exchange tubes can reduce the use of heat-exchange tubes, and then significantly reduce the overall cost of the heat exchanger assembly 1.
  • the heat exchange resistance is large.
  • the large pressure loss is not conducive to the circulating flow of the refrigerant.
  • the diameter of the heat exchange tube of the back-pipe heat exchanger 14 is set to be larger than that of the main heat exchanger.
  • the refrigerant When the heat exchanger component 1 is cooled, the refrigerant first enters the large-diameter heat exchange tube of the back-tube heat exchanger 14 and then splits into the small-diameter heat exchange tube of the main heat exchanger, that is, when the refrigerant changes from a gaseous state. In the process of being liquid, the contact area between the refrigerant and the heat exchange tube should be increased accordingly.
  • the refrigerant is first shunted in the small-diameter heat exchange tube of the main heat exchanger, and then aggregated into The large-diameter heat-exchange tubes of the back-tube heat exchanger 14 are compared and analyzed in Table 2 for the effect of the refrigerant flow in different tube diameters on the APF in the heat exchanger assembly 1 under heating conditions.
  • the refrigerant used in this embodiment flows through a small-diameter heat exchange tube and then a large-diameter heat exchange tube in the heating condition.
  • the energy efficiency of the method is the highest.
  • the heat exchanger tubes of the back-tube heat exchanger 14 adopt a diameter of ⁇ 7
  • the heat exchanger tubes of the main heat exchanger adopt a diameter of ⁇ 5.
  • the heat exchanger tubes of ⁇ 7 and ⁇ 5 are both The heat exchange tubes widely used in the prior art, therefore, the selection of the above two tube diameters is helpful to reduce the difficulty of obtaining the heat exchange tubes and reduce the manufacturing cost of the heat exchanger assembly 1.
  • the respective heat exchange tubes can also be specifically other tube diameter sizes.
  • the heat exchange tubes of the back tube heat exchanger 14 can also adopt a diameter of ⁇ 6. Limited to this.
  • the number of heat exchange tubes of the back-tube heat exchanger 14 is preferably 2 to 4, and in order to make the back-tube heat exchanger 14 is better set to face the air inlet on the casing 3, so that the back-pipe heat exchanger 14 is arranged near the front heat exchanger relative to the rear heat exchanger.
  • the second branch 22 flows through a part of the heat exchange tubes of the middle heat exchanger 12, and the first branch 21 flows through the remaining heat exchange tubes of the middle heat exchanger 12 and the front heat exchange. All heat exchange tubes of the heat exchanger 11. It can be understood that in such a setting, under the condition that the heat exchange tubes passing through the first branch 21 and the second branch 22 are similar, the design of the flow path can be simplified as much as possible to reduce the production difficulty of the main heat exchanger. It should be noted that this design is not limited to this. In other embodiments, the second branch 22 flows through a part of the heat exchange tubes of the front heat exchanger 11 and the middle heat exchanger 12, and the first branch 21 flows through the front changer. The remaining heat exchange tubes of the heat exchanger 11 and the middle heat exchanger 12.
  • the first branch 21 flows from the heat exchange tube in the middle of the second outer row 121, flows along the second outer row 121 toward one side of the front heat exchanger 11, and enters the first outer row through the first jumper pipe 17.
  • 111 flows through the entire first outer row 111 and the first inner row 112 in sequence, and flows out from the first inner row 112;
  • the second branch 22 flows in from the second outer row 121, and sequentially flows through the second outer row 121
  • the remaining part, and the entire second inner row 122 flows out from the second inner row 122.
  • the first branch 21 flows to the heat exchanger tube of the middle heat exchanger 12 closest to the front heat exchanger 11, and then enters the front heat exchanger 11 through the first jumper pipe 17, which is beneficial to reducing the first jumper pipe 17. And the gap between the front heat exchanger 11 and the middle heat exchanger 12. Specifically, the first branch 21 passes through the two heat exchange tubes of the second outer row 121 and enters the front heat exchanger 11 through the first crossover pipe 17. It should be noted that the present design is not limited to this. In other embodiments, the first branch circuit 21 may also flow in from the heat exchange tubes at other positions of the second outer row 121.
  • the second branch 22 flows in from a heat exchange tube adjacent to the heat transfer tube flowing into the first branch 21 on the second outer row 121 and faces the side of the rear heat exchanger 13 along the second outer row 121. flow. It can be understood that the first branch 21 and the second branch 22 flow along the two opposite sides of the second outer row 121 to share the heat exchange tubes of the second outer row 121. This arrangement prevents the second branch 22 from The heat exchange tubes of the second outer row 121 have been exhausted, and the flow direction must be changed, that is, the flow direction of the second branch 22 is simplified. Specifically, the second branch 22 enters the second inner row 122 after passing through the three heat exchange tubes of the second outer row 121. It should be noted that the present design is not limited to this.
  • the second branch 22 flows from the heat exchange tube at the rear end of the second outer row 121, and moves along the second outer row 121 toward one of the front heat exchangers 11.
  • the side flows to the heat exchange tube adjacent to the heat exchange tube in which the first branch 21 on the second outer row 121 flows.
  • first branch 21 enters the heat exchange tube of the first outer row 111 close to the middle heat exchanger 12 through the first jumper pipe 17 and flows through the entire first outer row 111 and the first inner row 112 in sequence, and then It flows out from the heat exchange tubes of the first inner row 112 near the middle heat exchanger 12.
  • the first branch 21 flows in from the upper end of the windward side of the front heat exchanger 11, and the air volume at this position is adapted to the higher energy of the refrigerant in the first branch 21 at this time to better Realizing the heat exchange of the refrigerant, and the way that the first branch 21 flows through the first outer row 111 from bottom to top and the first inner row 112 flows from bottom to top also simplifies the flow path in the front heat exchanger 11 design. It should be noted that this design is not limited to this. In other embodiments, the first branch 21 may also enter the front heat exchanger 11 from other heat exchange tubes of the first outer row 111, or from the first inner row 112. The other heat exchange tubes are discharged from the front heat exchanger 11.
  • the second branch 22 flows from the second outer row 121 to the heat exchange tube of the second inner row 122 near the rear heat exchanger 13 and flows along the second inner row 122 toward the side of the front heat exchanger 11, It then flows out from the heat exchange tubes of the second inner row 122 near the front heat exchanger 11. It can be understood that in this way, the second branch 22 can always keep flowing forward, and the design of the flow direction is simple, which is helpful to reduce the processing difficulty of the middle heat exchanger 12. It should be noted that this design is not limited to this. In other embodiments, the second branch 22 may also flow from the second outer row 121 to other heat exchange tubes of the second inner row 122, or from the second inner row 122. The other heat exchange tubes flow out of the heat exchanger 12.
  • the third branch line 23 flows in from the heat exchange tubes of the third outer row 131 near the middle heat exchanger 12 and sequentially flows through the entire third outer row 131 and the third inner row 132 and from the third inner row
  • the heat exchange tube of 132 near the middle heat exchanger 12 flows out.
  • the third branch 23 flows from the upper end of the windward side of the rear heat exchanger 13, and the air volume at this position is adapted to the higher energy of the refrigerant in the third branch 23 at this time to better
  • the heat exchange of refrigerant is carried out on the ground, and the way that the third branch 23 flows through the third outer row 131 from the top to the bottom and the third inner row 132 flows from the bottom to the top also simplifies the flow in the rear heat exchanger 13 Road design. It should be noted that this design is not limited to this.
  • the third branch 23 may also enter the rear heat exchanger 13 from other heat exchange tubes of the third outer row 131, or from the third inner row 132. The other heat exchange tubes are discharged after the heat exchanger 13.
  • Table 3 compares and analyzes the influence of the distribution method of the number of heat exchange tubes in the three branches on the APF.
  • the energy efficiency of the heat exchanger assembly 1 is the highest; and in this way, the difference between the number of the first branch 21 and the second branch 22 passing through the heat exchange tubes is 1, and the first branch
  • the difference between the number of channels 21 and the third branch 23 passing through the heat exchange tube is 1, and the difference between the number of the second branch 22 and the third branch 23 passing through the heat exchange tube is 0.
  • the energy efficiency of the heat exchanger assembly 1 is improved, and the difference between the number of heat exchange tubes passing between any two branches is less than or equal to 3.
  • the first branch circuit 21 flows in from the heat exchange tubes of the second outer row 121 near the front heat exchanger 11, flows along the second outer row 121 toward one side of the front heat exchanger 11 and passes through the first jumper pipe 17. Enters the first outer row 111 and flows through the entire first outer row 111 and the first inner row 112 in turn, and then enters the second inner row 122 through the second crossover pipe 18 and flows out from the second inner row 122; the second branch The path 22 flows in from the second outer row 121, flows through the remaining parts of the second outer row 121 and the second inner row 122 in sequence, and flows out from the second inner row 122.
  • the first branch 21 flows to the heat exchanger tube of the middle heat exchanger 12 closest to the front heat exchanger 11, and then enters the front heat exchanger 11 through the first jumper pipe 17, which is beneficial to reducing the first jumper pipe 17. And the gap between the front heat exchanger 11 and the middle heat exchanger 12. Specifically, the first branch 21 passes through a heat exchange tube of the second outer row 121 and enters the front heat exchanger 11 through the first crossover pipe 17. It should be noted that the present design is not limited to this. In other embodiments, the first branch circuit 21 may also flow in from the heat exchange tubes at other positions of the second outer row 121.
  • the second branch 22 flows in from a heat exchange tube adjacent to the heat transfer tube flowing into the first branch 21 on the second outer row 121 and faces the side of the rear heat exchanger 13 along the second outer row 121. flow. It can be understood that the first branch 21 and the second branch 22 flow along the two opposite sides of the second outer row 121 to share the heat exchange tubes of the second outer row 121. This arrangement prevents the second branch 22 from The heat exchange tubes of the second outer row 121 have been exhausted, and the flow direction must be changed, that is, the flow direction of the second branch 22 is simplified. Specifically, the second branch 22 enters the second inner row 122 after passing through the four heat exchange tubes of the second outer row 121. It should be noted that the present design is not limited to this.
  • the second branch 22 flows from the heat exchange tube at the rear end of the second outer row 121, and moves along the second outer row 121 toward one of the front heat exchangers 11.
  • the side flows to the heat exchange tube adjacent to the heat exchange tube in which the first branch 21 on the second outer row 121 flows.
  • first branch circuit 21 enters the heat exchange tube of the first outer row 111 adjacent to the middle heat exchanger 12 through the first jumper pipe 17 and flows through the entire first outer row 111 and the first inner row 112 in order to reach The heat exchange tubes of the first inner row 112 near the middle heat exchanger 12 enter the second inner row 122 through the second crossover pipe 18.
  • the first branch 21 flows in from the upper end of the windward side of the front heat exchanger 11, and the air volume at this position is adapted to the higher energy of the refrigerant in the first branch 21 at this time to better Realizing the heat exchange of the refrigerant, and the way that the first branch 21 flows through the first outer row 111 from bottom to top and the first inner row 112 flows from bottom to top also simplifies the flow path in the front heat exchanger 11
  • the first branch 21 enters the middle heat exchanger 12 from the heat exchanger tube of the front heat exchanger 11 near the middle heat exchanger 12 through the second jumper pipe 18, which is also beneficial to reduce the length of the second jumper pipe 18 And the gap between the front heat exchanger 11 and the middle heat exchanger 12.
  • the first branch 21 may also enter the front heat exchanger 11 from other heat exchange tubes of the first outer row 111, or from the first inner row 112.
  • the other heat exchange tubes enter the middle heat exchanger 12 through the second jumper tube 18.
  • the first branch circuit 21 enters the heat exchange tube of the second inner row 122 near the front heat exchanger 11 through the second jumper pipe 18, and flows along the second inner row 122 toward one side of the rear heat exchanger 13, It flows out from the heat exchange tube in the middle of the second inner row 122. It can be understood that in this way, the first branch line 21 enters from the heat exchange tube of the second inner row 122 close to the front heat exchanger 11, which is beneficial to reducing the length of the second crossover pipe 18, and the front heat exchanger 11 and the center exchange. The gap between the heaters 12. Specifically, the first branch 21 passes through the two heat exchange tubes of the second inner row 122 and exits the middle heat exchanger 12. It should be noted that the design is not limited to this. In other embodiments, the first branch 21 may also enter the middle heat exchanger 12 from other heat exchange tubes of the second inner row 122, or from the second inner row 122. The other heat exchange tubes are discharged from the heat exchanger 12.
  • the second branch 22 flows from the second outer row 121 to the heat exchange tube of the second inner row 122 near the rear heat exchanger 13 and flows along the second inner row 122 toward the side of the front heat exchanger 11, It then flows out from the heat exchange tube adjacent to the heat exchange tube flowing out of the first branch 21. It can be understood that in this way, the second branch 22 can always flow forward after entering the second inner row 122, and the flow direction is simple in design, which is helpful to reduce the processing difficulty of the middle heat exchanger 12. It should be noted that this design is not limited to this. In other embodiments, the second branch 22 may also flow from the second outer row 121 to other heat exchange tubes of the second inner row 122, or from the second inner row 122. The other heat exchange tubes flow out of the heat exchanger 12.
  • the third branch line 23 flows in from the heat exchange tubes of the third outer row 131 near the middle heat exchanger 12 and sequentially flows through the entire third outer row 131 and the third inner row 132 and from the third inner row
  • the heat exchange tube of 132 near the middle heat exchanger 12 flows out.
  • the third branch 23 flows from the upper end of the windward side of the rear heat exchanger 13, and the air volume at this position is adapted to the higher energy of the refrigerant in the third branch 23 at this time to better
  • the heat exchange of refrigerant is carried out on the ground, and the way that the third branch 23 flows through the third outer row 131 from the top to the bottom and the third inner row 132 flows from the bottom to the top also simplifies the flow in the rear heat exchanger 13 Road design. It should be noted that this design is not limited to this.
  • the third branch 23 may also enter the rear heat exchanger 13 from other heat exchange tubes of the third outer row 131, or from the third inner row 132. The other heat exchange tubes are discharged after the heat exchanger 13.
  • Table 4 compares and analyzes the influence of the distribution method of the number of heat exchange tubes in the three branches on the APF.
  • the energy efficiency of the heat exchanger assembly 1 is the highest; and in this way, the difference between the number of the first branch 21 and the second branch 22 passing through the heat exchange tubes is 2, and the first branch
  • the difference between the number of the tubes 21 and the third branch 23 passing through the heat exchange tube is 1, and the difference between the number of the second branch 22 and the third branch 23 passing the heat exchange tube is 1.
  • this also meets the previous requirements.
  • the energy efficiency of the heat exchanger assembly 1 is improved, and the difference between the number of heat exchange tubes passing between any two branches is less than or equal to 3.
  • the first branch 21 flows in from the heat exchange tubes of the first outer row 111 near the middle heat exchanger 12, flows through the entire first outer row 111 and the first inner row 112 in sequence, and reaches the first inner row 112.
  • the heat exchange tubes near the middle heat exchanger 12 enter the second inner row 122 through the second crossover pipe 18 and flow out from the second inner row 122.
  • the second branch 22 flows in from the second outer row 121 and flows in sequence. It passes through the entire second outer row 121 and the rest of the second inner row 122 and flows out from the second inner row 122.
  • the first branch 21 flows in from the upper end of the windward side of the front heat exchanger 11, and the air volume at this position is adapted to the higher energy of the refrigerant in the first branch 21 at this time to better Realizing the heat exchange of the refrigerant, and the way that the first branch 21 flows through the first outer row 111 from bottom to top and the first inner row 112 flows from bottom to top also simplifies the flow path in the front heat exchanger 11
  • the design, in addition, for the second branch 22 does not need to step into the front heat exchanger 11, which is helpful to reduce the difficulty of the flow path design. It should be noted that this design is not limited to this.
  • the first branch 21 may also flow in from other heat exchange tubes of the first outer row 111, or pass through other heat exchange tubes of the first inner row 112.
  • the second crossover pipe 18 enters the second inner row 122.
  • the second branch 22 flows in from the heat exchange tubes of the second outer row 121 near the front heat exchanger 11 and flows along the second outer row 121 to the replacement of the second outer row 121 near the rear heat exchanger 13
  • the heat pipe flows into the second inner row 122 again. It can be understood that in this way, the second branch 22 can flow through the heat exchange tubes of the entire second outer row 121 without changing the flow direction when the second outer row 121 flows.
  • the flow path is simple, which is beneficial to lowering the middle heat exchanger 12 Difficulty of processing. It should be noted that this design is not limited to this.
  • the second branch 22 flows from the heat exchange tube of the second outer row 121 near the rear heat exchanger 13 and flows along the second outer row 121 to The heat exchange tubes of the second outer row 121 near the front heat exchanger 11 flow into the second inner row 122 again.
  • the first branch circuit 21 enters the heat exchange tube of the second inner row 122 near the front heat exchanger 11 through the second jumper pipe 18, and flows along the second inner row 122 toward one side of the rear heat exchanger 13, It flows out from the heat exchange tube in the middle of the second inner row 122. It can be understood that in this way, the first branch line 21 enters from the heat exchange tube of the second inner row 122 close to the front heat exchanger 11, which is beneficial to reducing the length of the second crossover pipe 18, and the front heat exchanger 11 and the center exchange. The gap between the heaters 12. Specifically, the first branch 21 passes through the two heat exchange tubes of the second inner row 122 and exits the middle heat exchanger 12. It should be noted that the design is not limited to this. In other embodiments, the first branch 21 may also enter the middle heat exchanger 12 from other heat exchange tubes of the second inner row 122, or from the second inner row 122. The other heat exchange tubes are discharged from the heat exchanger 12.
  • the second branch 22 flows from the second outer row 121 into the heat exchange tube of the second inner row 122 near the rear heat exchanger 13 and flows along the second inner row 122 toward one side of the front heat exchange tube, and then It flows out from the heat exchange tube adjacent to the heat exchange tube which flows out of the first branch 21.
  • the second branch 22 After the second branch 22 enters the second inner row 122, it can always keep flowing forward, and the flow direction is simple in design, which is helpful to reduce the processing difficulty of the middle heat exchanger 12. It should be noted that this design is not limited to this.
  • the second branch 22 may also flow from the second outer row 121 to other heat exchange tubes of the second inner row 122, or from the second inner row 122.
  • the other heat exchange tubes flow out of the heat exchanger 12.
  • the third branch line 23 flows in from the heat exchange tube of the third outer row 131 near the middle heat exchanger 12 and sequentially flows through the entire third outer row 131 and the third inner row 132, and then from the third inner row
  • the heat exchange tube of 132 near the middle heat exchanger 12 flows out.
  • the third branch 23 flows from the upper end of the windward side of the rear heat exchanger 13, and the air volume at this position is adapted to the higher energy of the refrigerant in the third branch 23 at this time to better
  • the heat exchange of refrigerant is carried out on the ground, and the way that the third branch 23 flows through the third outer row 131 from the top to the bottom and the third inner row 132 flows from the bottom to the top also simplifies the flow in the rear heat exchanger 13 Road design. It should be noted that this design is not limited to this.
  • the third branch 23 may also enter the rear heat exchanger 13 from other heat exchange tubes of the third outer row 131, or from the third inner row 132. The other heat exchange tubes are discharged after the heat exchanger 13.
  • Table 5 compares and analyzes the influence of the distribution method of the number of heat exchange tubes in the three branches on the APF.
  • the present application also proposes an air conditioner, which includes an air conditioner outdoor unit and an air conditioner indoor unit.
  • an air conditioner indoor unit For a specific structure of the air conditioner indoor unit, refer to the foregoing embodiment. Since the air conditioner indoor unit adopts all the technical solutions of all the embodiments described above, It has at least all the beneficial effects brought by the technical solutions of the foregoing embodiments, and is not repeated here one by one.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)

Abstract

一种换热器组件（1），包括：主体换热器，包括前换热器（11）、中换热器（12）以及后换热器（13），前换热器（11）、中换热器（12）以及后换热器（13）均设置有至少两排换热管，中换热器（12）的换热管数量大于前换热器（11）和后换热器（13）；背管换热器（14）；换热器组件（1）的换热流路经过背管换热器（14）后分为第一支路（21）、第二支路（22）以及第三支路（23），第一支路（21）、第二支路（22）以及第三支路（23）均自主体换热器迎风侧的换热管朝背风侧的换热管流动；第一支路（21）流经前换热器（11）的换热管，第二支路（22）流经中换热器（12）的换热管，第三支路（23）流经后换热器（13）的换热管，且第一支路（21）和第三支路（23）中至少一者还跨经中换热器（12）的换热管设置。另外还公开了一种包括该换热器组件（1）的空调室内机。

Description

换热器组件和空调室内机
技术领域
本申请涉及空调产品技术领域，特别涉及一种换热器组件和空调室内机。
背景技术
随着国内外空调器能效标准不断提升，怎样提高空调器的换热器的换热效率成为亟待解决的问题。在众多的解决方案中，在全新设计空调器中使用换热效率高的换热器或用换热效率高的换热器对已批量生产的空调器的换热性能较低的换热器进行替换是比较有效的途径。
示例性技术中换热性能较好的空调换热器一般包括前换热器、中换热器以及后换热器，三者呈半包围设置，当空调换热器处于制冷工况时，制冷剂由三通管分为三路，分别进入前换热器、中换热器以及后换热器进行换热，然而，由于前换热器、中换热器以及后换热器受限于空调机壳内的长方形空间，因此，它们各自的尺寸也各不相同，以致各换热器内能够设置的换热管数量也都有一定差别，往往中换热器的尺寸是前换热器或后换热器的2倍甚至更多，相应地，中换热器内设置的换热管的数量也远远多于前换热器或后换热器，如此，制冷剂进入前换热器或后换热器后至流出空调换热器前，通过的换热管数量会远远小于制冷剂进入中换热器所通过的换热管数量，换言之，制冷剂在前换热器或后换热器中换热时很可能出现未充分换热即从室内换热器排出的情况，而在中换热器中换热时则又可能出现早已充分换热却仍继续流经换热管的情况；概括而言，即此种流路设计使得空调换热器的换热不均衡，降低了空调换热器的能效。
申请内容
本申请的主要目的是提出一种换热器组件，旨在改善示例性技术中空调换热器的中换热器与前换热器、后换热器的换热均衡性，提高空调换热器的能效。
为实现上述目的，本申请提出的换热器组件，包括：
主体换热器，呈半包围状设置；所述主体换热器包括前换热器、中换热器以及后换热器，所述前换热器、中换热器以及后换热器在进风方向上均设置有至少两排换热管，所述中换热器的换热管数量大于所述前换热器和后换热器；以及
背管换热器，安装于所述主体换热器的迎风侧；其中，
当所述换热器组件制冷时，所述换热器组件的换热流路经过所述背管换热器后分为第一支路、第二支路以及第三支路，所述第一支路、第二支路以及第三支路均自所述主体换热器迎风侧的换热管朝背风侧的换热管流动；所述第一支路流经所述前换热器的换热管，所述第二支路流经所述中换热器的换热管，所述第三支路流经所述后换热器的换热管，且所述第一支路和第三支路中至少一者还跨经所述中换热器的换热管设置。
可选地，所述第一支路、第二支路以及第三支路各自流经的换热管数量的两两差值小于或等于3。
可选地，所述前换热器、中换热器以及后换热器均设置有两排换热管，所述主体换热器的换热管总数量为18~22根。
可选地，所述第三支路流经所述后换热器的所有换热管，所述第二支路流经所述中换热器的部分换热管，所述第一支路流经所述中换热器剩余的换热管、及所述前换热器的所有换热管。
可选地，所述前换热器的换热管包括第一外排和第一内排，所述中换热器的换热管包括第二外排和第二内排，所述第一外排和第二外排位于所述主体换热器的迎风侧；
当所述换热器组件制冷时，所述第一支路从所述第二外排流入，沿所述第二外排流动并经第一跨接管进入所述第一外排，并依次流经整个所述第一外排和第一内排，并从所述第一内排流出；所述第二支路从所述第二外排流入，依次流经所述第二外排的剩余部分、以及整个第二内排，并从所述第二内排流出。
可选地，所述第一支路从所述第二外排中部的换热管流入，并沿所述第二外排朝所述前换热器的一侧流动，再经所述第一跨接管进入所述第一外排的靠近所述中换热器的换热管，并依次流经整个所述第一外排和第一内排，再从所述第一内排的靠近所述中换热器的换热管流出。
可选地，所述第二支路从与所述第二外排上第一支路流入的换热管相邻的换热管流入，并沿所述第二外排朝所述后换热器的一侧流动，再自所述第二外排流入所述第二内排的靠近所述后换热器的换热管，并沿所述第二内排朝所述前换热器的一侧流动，再从所述第二内排的靠近所述前换热器的换热管流出。
可选地，所述后换热器包括第三内排和第三外排，所述第三外排位于所述主体换热器的迎风侧；
所述第三支路从所述第三外排的靠近所述中换热器的换热管流入，并依次流经整个所述第三外排和第三内排，并从所述第三内排的靠近所述中换热器的换热管流出。
可选地，所述前换热器内的换热管包括第一外排和第一内排，所述中换热器内的换热管包括第二外排和第二内排，所述后换热器内的换热管包括第三外排和第三内排；所述第一外排、第二外排、第三外排均靠近所述主体换热器的迎风侧设置；
当所述换热器组件制冷时，所述第一支路从所述第一外排流入，并依次流经整个所述第一外排和第一内排，再经第一跨接管进入所述第二内排，并从所述第二内排流出；所述第二支路从所述第二外排流入，依次流经整个所述第二外排、及所述第二内排的剩余部分，并从所述第二内排流出；所述第三支路从所述第三外排流入，并依次流经整个第三外排和第三内排，并从所述第三内排流出；
可选地，所述第一支路从所述第一外排的靠近所述中换热器的换热管流入，依次流经整个所述第一外排和第一内排，到达所述第一内排的靠近所述中换热器的换热管，再经过所述第一跨接管进入所述第二内排；
可选地，所述前换热器的换热管包括第一外排和第一内排，所述中换热器的换热管包括第二外排和第二内排，所述后换热器的换热管包括第三外排和第三内排，所述第一外排、第二外排以及第三外排均靠近所述主体换热器的迎风侧设置；
当所述换热器组件制冷时，所述第一支路从所述第二外排流入，沿所述第二外排流动并经第一跨接管进入所述第一外排，并依次流经整个所述第一外排和第一内排，再经第二跨接管进入所述第二内排，并从所述第二内排流出；所述第二支路从所述第二外排流入，依次流经所述第二外排和第二内排的剩余部分，并从所述第二内排流出；所述第三支路从所述第三外排流入，并依次流经整个第三外排和第三内排，并从所述第三内排流出；
可选地，所述背管换热器的换热管管径大于所述主体换热器的换热管管径。
可选地，所述背管换热器安装于所述中换热器的迎风侧。
可选地，所述背管换热器相对所述后换热器靠近所述前换热器设置。
可选地，所述背管换热器的换热管数量为2~4根。
本申请还提出一种空调室内机，包括换热器组件、以及用以容置所述换热器组件的机壳，所述换热器组件包括：
主体换热器，呈半包围状设置；所述主体换热器包括前换热器、中换热器以及后换热器，所述前换热器、中换热器以及后换热器在进风方向上均设置有至少两排换热管，所述中换热器的换热管数量大于所述前换热器和后换热器；以及
背管换热器，安装于所述主体换热器的迎风侧；其中，
当所述换热器组件制冷时，所述换热器组件的换热流路经过所述背管换热器后分为第一支路、第二支路以及第三支路，所述第一支路、第二支路以及第三支路均自所述主体换热器迎风侧的换热管朝背风侧的换热管流动；所述第一支路流经所述前换热器的换热管，所述第二支路流经所述中换热器的换热管，所述第三支路流经所述后换热器的换热管，且所述第一支路和第三支路中至少一者还跨经所述中换热器的换热管设置。
可选地，所述机壳沿前后向的宽度尺寸小于800mm，所述机壳沿上下向的高度尺寸小于295mm。
可选地，所述换热器组件设于所述机壳内时，所述后换热器的排布方向与上下方向的夹角范围38°~48°。
可选地，所述换热器组件设于所述机壳内时，所述中换热器和前换热器的排布方向与上下方向的夹角范围45°~55°。
可选地，所述中换热器与后换热器相互靠近的一端互相抵接；或
所述中换热器与后换热器相互靠近的一端之间存有间隙，所述空调室内机还包括挡风板，所述挡风板跨接于所述中换热器和后换热器相互靠近的一端的迎风侧之间。
本申请技术方案的换热器组件包括主体换热器和设于主体换热器迎风侧的背管换热器，主体换热器包括前换热器、中换热器以及后换热器，换热器组件制冷时，经过背管换热器后的换热流路分流为第一支路、第二支路以及第三支路，第一支路流经前换热器，第二支路流经中换热器，第三支路流经后换热器，通过将第一支路和第三支路中的一者跨经中换热器的换热管，如此改善流路之后，使得中换热器中一部分的换热管可以用于供经过前换热器或后换热器换热管的制冷剂继续通过，避免了第一支路仅通过前换热器的换热管或第三支路仅通过后换热器的换热管可能出现的制冷剂换热不充分（由于前换热器和后换热器的换热管较少），以及第二支路仅通过中换热器的换热管可能出现的结构浪费问题（由于中换热器的换热管较多），同时也使得前换热器、后换热器与中换热器之间的换热效果更为均衡，有效提升了换热器组件的能效。
附图说明
为了更清楚地说明本申请实施例或现有技术中的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图示出的结构获得其他的附图。
图1为本申请空调室内机一实施例的结构示意图；
图2为本申请换热器组件第一实施例的流路示意图；
图3为本申请换热器组件第二实施例的流路示意图；
图4为本申请换热器组件第三实施例的流路示意图。
附图标号说明：
标号 名称 标号 名称
1 换热器组件 11 前换热器
111 第一外排 112 第一内排
12 中换热器 121 第二外排
122 第二内排 13 后换热器
131 第三外排 132 第三内排
14 背管换热器 15 分配器
16 挡风板 17 第一跨接管
18 第二跨接管 2 换热流路
21 第一支路 22 第二支路
23 第三支路 24 第一制冷剂总管
25 第二制冷剂总管 3 机壳
4 贯流风轮
本申请目的的实现、功能特点及优点将结合实施例，参照附图做进一步说明。
具体实施方式
下面将结合本申请实施例中的附图，对本申请实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本申请的一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
需要说明，若本申请实施例中有涉及方向性指示（诸如上、下、左、右、前、后……），则该方向性指示仅用于解释在某一特定姿态（如附图所示）下各部件之间的相对位置关系、运动情况等，如果该特定姿态发生改变时，则该方向性指示也相应地随之改变。
另外，若本申请实施例中有涉及“第一”、“第二”等的描述，则该“第一”、“第二”等的描述仅用于描述目的，而不能理解为指示或暗示其相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。另外，各个实施例之间的技术方案可以相互结合，但是必须是以本领域普通技术人员能够实现为基础，当技术方案的结合出现相互矛盾或无法实现时应当认为这种技术方案的结合不存在，也不在本申请要求的保护范围之内。
本申请提出一种换热器组件及具有该换热器组件的空调室内机，当然，于其他实施例中，该换热器组件也可应用于空调一体机或空调室外机等，本设计不限于此。
本实施例中，参照图1，该空调室内机为壁挂式空调室内机，其具体包括机壳3、设于机壳3内的贯流风轮4，当然，换热器组件1也设置在机壳3内，且位于机壳3上的进风口和贯流风轮4之间，以对贯流风轮4吸入的空气进行换热。容易理解的，本实施例中，以壁挂式空调室内机装配完成后朝向用户的一侧为前，面向墙壁的一侧为后，而壁挂式空调室内机采用常规的上进风下出风口的运行方式，即换热器组件1位于贯流风轮4的上侧。应当说明的是，本设计不限于此，于其他实施例中，空调室内机也可具体为立式室内空调等。
在本申请实施例中，参照图1至图4，该换热器组件1包括：
主体换热器，呈半包围环绕贯流风轮4设置；主体换热器包括前换热器11、中换热器12以及后换热器13，前换热器11、中换热器12以及后换热器13在进风方向上均设置有至少两排换热管，中换热器12的换热管数量大于前换热器11和后换热器13；以及
背管换热器14，安装于主体换热器的迎风侧；
本实施例中，前换热器11、中换热器12以及后换热器13在进风方向上均设置有两排换热管，既避免换热管排数过少以致换热不充分，又防止换热管设置过多以致结构的浪费；当然，于其他实施例中，为满足各换热器不同的换热需求，其也可在进风风向上设置三排、甚至四排换热管，本设计不限于此。具体地，前换热器11的换热管包括第一外排111和第一内排112，中换热器12的换热管包括第二外排121和第二内排122，后换热器13的换热管包括第三外排131和第三内排132，第一外排111、第二外排121以及第三外排131均位于主体换热器的迎风侧。容易理解的是，在主体换热器的迎风侧增设背管换热器14也是为了增强换热器组件1的换热能力，不失一般性，为了将背管换热器14的能效发挥到最大化，将其安装于迎风面积最大的中换热器12的迎风侧。特别地，应当尽量避免中换热器12与后换热器13相互靠近的一端之间存有间隙，本实施例中，受限于空调室内机特殊的机壳尺寸，中换热器12与后换热器13相互靠近的一端之间存有间隙，为了避免从进风口进入的空气未通过换热器组件1而直接进入贯流风轮4，本实施例中，在中换热器12与后换热器13的迎风侧之间还跨接有挡风板16；例如但不限于，挡风板16的两端通过海绵分别贴合安装于中换热器12和后换热器13上，以在实现挡风板16与换热器连接的同时，保证挡风板16与换热器接触部分的密封性，同时海绵贴合的方式，也有利于用户在需要维修或者更换换热器组件1时，对挡风板16进行拆卸；当然，于其他实施例中，挡风板16还可通过螺钉锁附的方式安装于中换热器12和后换热器13，本设计不限于此。另外，若前换热器11与中换热器12之间也存有较大的间隙，同样可以两者之间增设挡风板16，以避免出现换热器组件1漏风的情况。
可以理解，空调换热循环系统中除了位于室内的换热器组件1还有室外换热器、压缩机等。本实施例中，背管换热器14一端与主体换热器相连，另一端与第一制冷剂总管24相连，第一制冷剂总管24用以与室外换热器相接。
本实施例中，参照图1至图4，当换热器组件1制冷时，压缩机送出的制冷剂先经过室外换热器换热，再通过第一制冷剂总管24进入到背管换热器14，经过背管换热器14后分为第一支路21、第二支路22以及第三支路23，第一支路21、第二支路22以及第三支路23均自主体换热器迎风侧的换热管朝背风侧的换热管流动；第一支路21和第二支路22分摊前换热器11和中换热器12的所有换热管，且第一支路21和第二支路22中至少一者跨经前换热器11和中换热器12的换热管设置，第三支路23流经后换热器13的所有换热管，第一支路21、第二支路22以及第三支路23在流出主体换热器后汇集在一第二制冷剂总管25，并流回到压缩机；当换热器组件1制热时，压缩机送出的制冷剂先通过第二制冷剂总管25进入换热器组件1，分别流经第一支路21、第二支路22以及第三支路23完成换热后，汇集并流过背管换热器14，之后再通过第一制冷剂总管24进入室外换热器换热，最后流回压缩机。需要说明的是，本设计不限于此，于其他实施例中，第一支路21流经前换热器11的所有换热管，而第二支路22与第三支路23分摊中换热器12和后换热器13的所有换热管，且第二支路22和第三支路23中至少一者跨经中换热器12和后换热器13的换热管设置。不失一般性，当换热器组件1制冷时，制冷剂经过背管换热器14后通过一分配器15分流为上述第一支路21、第二支路22以及第三支路23，当然，于其他实施例中，制冷剂也可通过笛形管等结构进行分流，本设计对此不做限制。
首先，对于本实施例中换热器组件1的流路设计，应当理解的是，在制冷工况下，第一支路21、第二支路22以及第三支路23上均采用从外侧（迎风侧）的换热管向内侧（背风侧）的换热管的流向原则，以提高换热温差，最大限度地改善换热效率，表1中对比分析了换热器组件1在制冷工况下从外侧换热管逐渐进入内侧换热管的流路与其他形式流路对APF（能效比）的影响。
输入管进入方式 APF
输入管中三路均由外侧进入内侧 6.42
输入管中两路由外侧进入内侧 6.25
输入管中两路由外侧进入内侧 6.07
表1
对比表1中不同流路形式与APF的对应关系可知，本实施例采用的三路均由外侧换热管朝内侧换热管流动的流路形式的能效是最高的。
而为了解决背景技术中所提及的“由于机壳3尺寸限制，以致前换热器11与中换热器12的换热管数量差距大，而制冷剂各自对前换热器11和中换热器12换热，导致换热不均衡、能效低”的技术问题，本实施例中换热器12组件1的流路设计还强调第一支路21和第二支路22分摊前换热器11和中换热器12的换热管，且第一支路21和第二支路22中至少一者设置为跨接于前换热器11和中换热器12的换热管之间，即不再将流路限定于只流过前换热器11或中换热器12，而是将两者的部分换热管进行串联，如此，既能有效弥补前换热器11的换热不足，又能避免中换热器12的结构浪费，从而有效实现前换热器11与中换热器12之间的换热均衡、及其能效的提高。
本实施例中，控制第一支路21和第二支路22各自流经的换热管数量的差值小于或等于3，以避免两者之间的换热功效差别过大，影响前换热器11和中换热器12之间的换热均衡性。特别地，控制第一支路21、第二支路22以及第三支路23各自流经的换热管数量的两两差值小于或等于3，如此，即可实现前换热器11、中换热器12、以及后换热器13三者之间的换热平衡，提升换热器组件1的整体能效。
在日常生活中，由于用户对家居空间的不同设计，往往会对壁挂式空调室内机的机壳3尺寸提出相关的要求，本实施例中，机壳3沿前后向的宽度尺寸L小于800mm，机壳3沿上下向的高度尺寸H小于295mm；对于适配该机壳3尺寸的换热器组件1，将主体换热器内的换热管总数量设为18~22根，以在有限的安装空间内保证换热器组件1维持在较高的能效，特别的，本实施例中，主体换热器的换热管数量为20。另外，限定在如此尺寸范围的机壳3内，综合考虑贯流风轮4的能效以及空间占用，贯流风轮4的直径D选取在115mm~125mm之间，且主体换热器的内侧面与贯流风轮4外侧面之间的间距S保持在大于10mm，而为了保证主体换热器半环绕贯流风轮4，能达到更好的提高换热能效的效果、以及凝露排水的可靠设计，保持后换热器13与上下方向的夹角处于38°~48°，中换热器12和前换热器11与上下方向的夹角处于45°~55°。
本申请技术方案的换热器组件1包括主体换热器和设于主体换热器迎风侧的背管换热器14，主体换热器包括前换热器11、中换热器12以及后换热器13，换热器组件1制冷时，经过背管换热器14后的换热流路2分流为第一支路21、第二支路22以及第三支路23，第一支路21流经前换热器11，第二支路22流经中换热器12，第三支路23流经后换热器13，通过将第一支路21和第三支路23中的一者跨经中换热器12的换热管，如此改善流路之后，使得中换热器12中一部分的换热管可以用于供经过前换热器11或后换热器13换热管的制冷剂继续通过，避免了第一支路21仅通过前换热器11的换热管或第三支路23仅通过后换热器13的换热管可能出现的制冷剂换热不充分（由于前换热器11和后换热器13的换热管较少），以及第二支路22仅通过中换热器12的换热管可能出现的结构浪费问题（由于中换热器12的换热管较多），同时也使得前换热器11、后换热器12与中换热器13之间的换热效果更为均衡，有效提升了换热器组件的能效。
众所周知，采用小管径的换热管能减少换热管的用料，继而显著地降低换热器组件1的整体成本，但是制冷剂通过小管径的换热管时，换热阻力大，压力损失大，不利于制冷剂的循环流动。本实施例中，综合考虑换热器组件1的成本和制冷剂循环流动效率问题，将背管换热器14的换热管管径设置为大于主体换热器的换热管管径，如此，换热器组件1制冷时，制冷剂先进入背管换热器14的大管径换热管，然后再分流进入主体换热器的小管径换热管，即在制冷剂由气态变化为液态的过程中，对应增大制冷剂与换热管的接触面积；换热器组件1制热时，制冷剂先分流在主体换热器的小管径换热管内换热，然后汇总进入背管换热器14的大管径换热管，表2中对比分析了换热器组件1在制热工况下制冷剂在不同管径流动方式对APF的影响。
制热时制冷剂不同管径流动方式 APF
先进入大管径后进入小管径 5.72
先进入小管径后进入大管径 6.46
表2
对比表2中不同流路形式与APF的对应关系可知，本实施例采用的在制热工况下将制冷剂先经过小管径的换热管，再经过大管径的换热管的流动方式的能效是最高的。不失一般性，背管换热器14的换热管采用φ7的管径，而主体换热器的换热管采用φ5的管径，可以理解，φ7和φ5管径的换热管都是现有技术中广泛使用的换热管，因此，选取以上两种管径的换热管，有利于降低换热管的获取难度，降低换热器组件1的制造成本；当然，于其他实施例中，背管换热器14、主体换热器各自的换热管也可具体为其他管径尺寸，例如背管换热器14的换热管还可采用φ6的管径等，本设计不限于此。另外，本实施例中，兼顾于换热器组件的能效需求和机壳3的尺寸限制，背管换热器14的换热管数量优选为2~4根，而且为了使背管换热器14更好地面向机壳3上的进风口设置，使背管换热器14相对后换热器靠近前换热器设置。
进一步地，参照图1至图4，第二支路22流经中换热器12的部分换热管，第一支路21流经中换热器12剩余的换热管、及前换热器11的所有换热管。可以理解，如此设置，在保证第一支路21和第二支路22通过的换热管相近的情况下，可尽量简化流路的设计，以降低主体换热器的生产难度。需要说明的是，本设计不限于此，于其他实施例中，第二支路22流经前换热器11和中换热器12的部分换热管，第一支路21流经前换热器11和中换热器12剩余的换热管。
以下介绍主体换热器的具体流路设计，以换热器组件1处于制冷工况下为例，在本申请的第一实施例中：
参照图2，第一支路21从第二外排121中部的换热管流入，沿第二外排121朝前换热器11的一侧流动并经第一跨接管17进入第一外排111，并依次流经整个第一外排111和第一内排112，并从第一内排112流出；第二支路22从第二外排121流入，依次流经第二外排121的剩余部分、以及整个第二内排122，并从第二内排122流出。可以理解，第一支路21流动至中换热器12最靠近前换热器11的换热管，再通过第一跨接管17进入前换热器11，有利于减小第一跨接管17的长度、及前换热器11与中换热器12之间的间隙。具体地，第一支路21经过第二外排121的两根换热管后经第一跨接管17进入前换热器11。需要说明的是，本设计不限于此，于其他实施例中，第一支路21也可从第二外排121其他位置的换热管流入。
进一步地，第二支路22从与第二外排121上第一支路21流入的换热管相邻的换热管流入，并沿第二外排121朝后换热器13的一侧流动。可以理解，第一支路21和第二支路22分别沿第二外排121的两相对侧流动，以分摊第二外排121的换热管，如此设置，避免了第二支路22为了流尽第二外排121的换热管，而必须改变其流动方向，即简化了第二支路22的流向。具体地，第二支路22经过第二外排121的三根换热管后进入第二内排122。应当说明的是，本设计不限于此，于其他实施例中，第二支路22从第二外排121最后端的换热管流入，并沿第二外排121朝前换热器11的一侧流动至与第二外排121上第一支路21流入的换热管相邻的换热管。
进一步地，第一支路21经第一跨接管17进入第一外排111的靠近中换热器12的换热管，并依次流经整个第一外排111和第一内排112，再从第一内排112的靠近中换热器12的换热管流出。可以理解，如此设置，第一支路21从前换热器11迎风侧的上端处流入，该位置处的风量适配于第一支路21内制冷剂此时较高的能量，以更好地实现制冷剂的换热，而将第一支路21由上至下流完第一外排111并由下至上流完第一内排112的方式，也简化了前换热器11中的流路设计。应当说明的是，本设计不限于此，于其他实施例中，第一支路21也可从第一外排111的其他换热管进入前换热器11，或者从第一内排112的其他换热管排出前换热器11。
进一步地，第二支路22自第二外排121流入第二内排122的靠近后换热器13的换热管，并沿第二内排122朝前换热器11的一侧流动，再从第二内排122的靠近前换热器11的换热管流出。可以理解，如此设置，第二支路22始终保持朝前流动即可，流向设计简单，有利于降低中换热器12的加工难度。需要说明的是，本设计不限于此，于其他实施例中，第二支路22也可自第二外排121流入第二内排122的其他换热管，或从第二内排122的其他换热管流出中换热器12。
进一步地，第三支路23从第三外排131的靠近中换热器12的换热管流入，并依次流经整个第三外排131和第三内排132，并从第三内排132的靠近中换热器12的换热管流出。可以理解，如此设置，第三支路23从后换热器13迎风侧的上端处流入，该位置处的风量适配于第三支路23内制冷剂此时较高的能量，以更好地实现制冷剂的换热，而将第三支路23由上至下流完第三外排131并由下至上流完第三内排132的方式，也简化了后换热器13中的流路设计。应当说明的是，本设计不限于此，于其他实施例中，第三支路23也可从第三外排131的其他换热管进入后换热器13，或者从第三内排132的其他换热管排出后换热器13。
基于以上本实施例中主体换热器的具体流路设计，表3中对比分析了三条支路中换热管根数的分配方式对APF的影响。
三支路（1,2,3支路）中铜管根数分配方式 APF
8根+8根+4根 6.02
9根+3根+8根 5.81
3根+9根+8根 5.87
6根+7根+7根 6.64
表3
对比表3中换热管根数的分配方式与APF的对应关系可知，优选采用第一支路21通过6根换热管、第二支路22通过7根换热管以及第三支路23通过7根换热管的方案，以使换热器组件1的能效最高；而如此设置，第一支路21与第二支路22通过换热管的根数差值为1，第一支路21与第三支路23通过换热管的根数差值为1，第二支路22与第三支路23通过换热管的根数差值为0，显然，这也符合之前为了提高换热器组件1能效，而对任意两支路之间通过换热管数量差值所作的小于或等于3的限定。
在本申请的第二实施例中：
参照图3，第一支路21从第二外排121靠近前换热器11的换热管流入，沿第二外排121朝前换热器11的一侧流动并经第一跨接管17进入第一外排111，并依次流经整个第一外排111和第一内排112，再经第二跨接管18进入第二内排122，并从第二内排122流出；第二支路22从第二外排121流入，依次流经第二外排121和第二内排122的剩余部分，并从第二内排122流出。可以理解，第一支路21流动至中换热器12最靠近前换热器11的换热管，再通过第一跨接管17进入前换热器11，有利于减小第一跨接管17的长度、及前换热器11与中换热器12之间的间隙。具体地，第一支路21经过第二外排121的一根换热管后经第一跨接管17进入前换热器11。需要说明的是，本设计不限于此，于其他实施例中，第一支路21也可从第二外排121其他位置的换热管流入。
进一步地，第二支路22从与第二外排121上第一支路21流入的换热管相邻的换热管流入，并沿第二外排121朝后换热器13的一侧流动。可以理解，第一支路21和第二支路22分别沿第二外排121的两相对侧流动，以分摊第二外排121的换热管，如此设置，避免了第二支路22为了流尽第二外排121的换热管，而必须改变其流动方向，即简化了第二支路22的流向。具体地，第二支路22经过第二外排121的四根换热管后进入第二内排122。应当说明的是，本设计不限于此，于其他实施例中，第二支路22从第二外排121最后端的换热管流入，并沿第二外排121朝前换热器11的一侧流动至与第二外排121上第一支路21流入的换热管相邻的换热管。
进一步地，第一支路21经第一跨接管17进入第一外排111的靠近中换热器12的换热管，并依次流经整个第一外排111和第一内排112，到达第一内排112的靠近中换热器12的换热管，再经第二跨接管18进入第二内排122。可以理解，如此设置，第一支路21从前换热器11迎风侧的上端处流入，该位置处的风量适配于第一支路21内制冷剂此时较高的能量，以更好地实现制冷剂的换热，而将第一支路21由上至下流完第一外排111并由下至上流完第一内排112的方式，也简化了前换热器11中的流路设计，另外，第一支路21从前换热器11的靠近中换热器12的换热管通过第二跨接管18进入中换热器12，也有利于减小第二跨接管18的长度、及前换热器11与中换热器12之间的间隙。应当说明的是，本设计不限于此，于其他实施例中，第一支路21也可从第一外排111的其他换热管进入前换热器11，或者从第一内排112的其他换热管经第二跨接管18进入中换热器12。
进一步地，第一支路21经第二跨接管18进入第二内排122的靠近前换热器11的换热管，并沿第二内排122朝后换热器13的一侧流动，再从第二内排122中部的换热管流出。可以理解，如此设置，第一支路21从第二内排122靠近前换热器11的换热管进入，有利于减小第二跨接管18的长度、及前换热器11与中换热器12之间的间隙。具体地，第一支路21经过第二内排122的两根换热管后排出中换热器12。应当说明的是，本设计不限于此，于其他实施例中，第一支路21也可从第二内排122的其他换热管进入中换热器12，或者从第二内排122的其他换热管排出中换热器12。
进一步地，第二支路22自第二外排121流入第二内排122的靠近后换热器13的换热管，并沿第二内排122朝前换热器11的一侧流动，再从与第一支路21流出的换热管相邻的换热管流出。可以理解，如此设置，第二支路22进入第二内排122后始终保持朝前流动即可，流向设计简单，有利于降低中换热器12的加工难度。需要说明的是，本设计不限于此，于其他实施例中，第二支路22也可自第二外排121流入第二内排122的其他换热管，或从第二内排122的其他换热管流出中换热器12。
进一步地，第三支路23从第三外排131的靠近中换热器12的换热管流入，并依次流经整个第三外排131和第三内排132，并从第三内排132的靠近中换热器12的换热管流出。可以理解，如此设置，第三支路23从后换热器13迎风侧的上端处流入，该位置处的风量适配于第三支路23内制冷剂此时较高的能量，以更好地实现制冷剂的换热，而将第三支路23由上至下流完第三外排131并由下至上流完第三内排132的方式，也简化了后换热器13中的流路设计。应当说明的是，本设计不限于此，于其他实施例中，第三支路23也可从第三外排131的其他换热管进入后换热器13，或者从第三内排132的其他换热管排出后换热器13。
基于以上本实施例中主体换热器的具体流路设计，表4中对比分析了三条支路中换热管根数的分配方式对APF的影响。
三支路（1,2,3支路）中铜管根数分配方式 APF
9根+9根+3根 5.95
9根+3根+9根 5.86
8根+9根+4根 6.11
8根+6根+7根 6.42
表4
对比表4中换热管根数的分配方式与APF的对应关系可知，优选采用第一支路21通过8根换热管、第二支路22通过6根换热管以及第三支路23通过7根换热管的方案，以使换热器组件1的能效最高；而如此设置，第一支路21与第二支路22通过换热管的根数差值为2，第一支路21与第三支路23通过换热管的根数差值为1，第二支路22与第三支路23通过换热管的根数差值为1，显然，这也符合之前为了提高换热器组件1能效，而对任意两支路之间通过换热管数量差值所作的小于或等于3的限定。
在本申请的第三实施例中：
参照图4，第一支路21从第一外排111的靠近中换热器12的换热管流入，依次流经整个第一外排111和第一内排112，到达第一内排112的靠近中换热器12的换热管，再经第二跨接管18进入第二内排122，并从第二内排122流出；第二支路22从第二外排121流入，依次流经整个第二外排121、及第二内排122的剩余部分，并从第二内排122流出。可以理解，如此设置，第一支路21从前换热器11迎风侧的上端处流入，该位置处的风量适配于第一支路21内制冷剂此时较高的能量，以更好地实现制冷剂的换热，而将第一支路21由上至下流完第一外排111并由下至上流完第一内排112的方式，也简化了前换热器11中的流路设计，另外，对于第二支路22其不需要跨入前换热器11内，有利于降低其流路设计的难度。应当说明的是，本设计不限于此，于其他实施例中，第一支路21也可从第一外排111的其他换热管流入，或从第一内排112的其他换热管通过第二跨接管18进入第二内排122。
进一步地，第二支路22从第二外排121的靠近前换热器11的换热管流入，并沿第二外排121流动至第二外排121的靠近后换热器13的换热管，再流入第二内排122。可以理解，如此设置，第二支路22在第二外排121流动时无需改变流向，即可流经整个第二外排121的换热管，流路简单，有利于降低中换热器12的加工难度。应当说明的是，本设计不限于此，于其他实施例中，第二支路22从第二外排121的靠近后换热器13的换热管流入，并沿第二外排121流动至第二外排121的靠近前换热器11的换热管，再流入第二内排122。
进一步地，第一支路21经第二跨接管18进入第二内排122的靠近前换热器11的换热管，并沿第二内排122朝后换热器13的一侧流动，再从第二内排122中部的换热管流出。可以理解，如此设置，第一支路21从第二内排122靠近前换热器11的换热管进入，有利于减小第二跨接管18的长度、及前换热器11与中换热器12之间的间隙。具体地，第一支路21经过第二内排122的两根换热管后排出中换热器12。应当说明的是，本设计不限于此，于其他实施例中，第一支路21也可从第二内排122的其他换热管进入中换热器12，或者从第二内排122的其他换热管排出中换热器12。
进一步地，第二支路22自第二外排121流入第二内排122的靠近后换热器13的换热管，并沿第二内排122朝前换热管的一侧流动，再从与第一支路21流出的换热管相邻的换热管流出。第二支路22进入第二内排122后始终保持朝前流动即可，流向设计简单，有利于降低中换热器12的加工难度。需要说明的是，本设计不限于此，于其他实施例中，第二支路22也可自第二外排121流入第二内排122的其他换热管，或从第二内排122的其他换热管流出中换热器12。
进一步地，第三支路23从第三外排131的靠近中换热器12的换热管流入，并依次流经整个第三外排131和第三内排132，再从第三内排132的靠近中换热器12的换热管流出。可以理解，如此设置，第三支路23从后换热器13迎风侧的上端处流入，该位置处的风量适配于第三支路23内制冷剂此时较高的能量，以更好地实现制冷剂的换热，而将第三支路23由上至下流完第三外排131并由下至上流完第三内排132的方式，也简化了后换热器13中的流路设计。应当说明的是，本设计不限于此，于其他实施例中，第三支路23也可从第三外排131的其他换热管进入后换热器13，或者从第三内排132的其他换热管排出后换热器13。
基于以上本实施例中主体换热器的具体流路设计，表5中对比分析了三条支路中换热管根数的分配方式对APF的影响。
三支路（1,2,3支路）中铜管根数分配方式 APF
9根+8根+4根 6.05
9根+4根+8根 5.88
4根+9根+8根 5.87
7根+7根+7根 6.48
表5
对比表5中换热管根数的分配方式与APF的对应关系可知，优选采用第一支路21通过7根换热管、第二支路22通过7根换热管以及第三支路23通过7根换热管的方案，以使换热器组件1的能效最高；而如此设置，第一支路21与第二支路22通过换热管的根数差值为0，第一支路21与第三支路23通过换热管的根数差值为0，第二支路22与第三支路23通过换热管的根数差值为0，显然，这也符合之前为了提高换热器组件1能效，而对任意两支路之间通过换热管数量差值所作的小于或等于3的限定。
本申请还提出一种空调器，该空调器包括空调室外机和空调室内机，该空调室内机的具体结构参照上述实施例，由于本空调室内机采用了上述所有实施例的全部技术方案，因此至少具有上述实施例的技术方案所带来的所有有益效果，在此不再一一赘述。
以上所述仅为本申请的优选实施例，并非因此限制本申请的专利范围，凡是在本申请的申请构思下，利用本申请说明书及附图内容所作的等效结构变换，或直接/间接运用在其他相关的技术领域均包括在本申请的专利保护范围内。

Claims (20)

  1. 一种换热器组件，用于空调室内机，其中，包括：
    主体换热器，呈半包围状设置；所述主体换热器包括前换热器、中换热器以及后换热器，所述前换热器、中换热器以及后换热器在进风方向上均设置有至少两排换热管，所述中换热器的换热管数量大于所述前换热器和后换热器；以及
    背管换热器，安装于所述主体换热器的迎风侧；其中，
    当所述换热器组件制冷时，所述换热器组件的换热流路经过所述背管换热器后分为第一支路、第二支路以及第三支路，所述第一支路、第二支路以及第三支路均自所述主体换热器迎风侧的换热管朝背风侧的换热管流动；所述第一支路流经所述前换热器的换热管，所述第二支路流经所述中换热器的换热管，所述第三支路流经所述后换热器的换热管，且所述第一支路和第三支路中至少一者还跨经所述中换热器的换热管设置。
  2. 如权利要求1所述的换热器组件，其中，所述第一支路、第二支路以及第三支路各自流经的换热管数量的两两差值小于或等于3。
  3. 如权利要求2所述的换热器组件，其中，所述前换热器、中换热器以及后换热器均设置有两排换热管，所述主体换热器的换热管总数量为18~22根。
  4. 如权利要求1所述的换热器组件，其中，所述第三支路流经所述后换热器的所有换热管，所述第二支路流经所述中换热器的部分换热管，所述第一支路流经所述中换热器剩余的换热管、及所述前换热器的所有换热管。
  5. 如权利要求4所述的换热器组件，其中，所述前换热器的换热管包括第一外排和第一内排，所述中换热器的换热管包括第二外排和第二内排，所述第一外排和第二外排位于所述主体换热器的迎风侧；
    当所述换热器组件制冷时，所述第一支路从所述第二外排流入，沿所述第二外排流动并经第一跨接管进入所述第一外排，并依次流经整个所述第一外排和第一内排，并从所述第一内排流出；所述第二支路从所述第二外排流入，依次流经所述第二外排的剩余部分、以及整个第二内排，并从所述第二内排流出。
  6. 如权利要求5所述的换热器组件，其中，所述第一支路从所述第二外排中部的换热管流入，并沿所述第二外排朝所述前换热器的一侧流动，再经所述第一跨接管进入所述第一外排的靠近所述中换热器的换热管，并依次流经整个所述第一外排和第一内排，再从所述第一内排的靠近所述中换热器的换热管流出。
  7. 如权利要求6所述的换热器组件，其中，所述第二支路从与所述第二外排上第一支路流入的换热管相邻的换热管流入，并沿所述第二外排朝所述后换热器的一侧流动，再自所述第二外排流入所述第二内排的靠近所述后换热器的换热管，并沿所述第二内排朝所述前换热器的一侧流动，再从所述第二内排的靠近所述前换热器的换热管流出。
  8. 如权利要求4所述的换热器组件，其中，所述后换热器包括第三内排和第三外排，所述第三外排位于所述主体换热器的迎风侧；
    所述第三支路从所述第三外排的靠近所述中换热器的换热管流入，并依次流经整个所述第三外排和第三内排，并从所述第三内排的靠近所述中换热器的换热管流出。
  9. 如权利要求1所述的换热器组件，其中，所述前换热器的换热管包括第一外排和第一内排，所述中换热器的换热管包括第二外排和第二内排，所述后换热器的换热管包括第三外排和第三内排，所述第一外排、第二外排以及第三外排均靠近所述主体换热器的迎风侧设置；
    当所述换热器组件制冷时，所述第一支路从所述第一外排流入，并依次流经整个所述第一外排和第一内排，再经第一跨接管进入所述第二内排，并从所述第二内排流出；所述第二支路从所述第二外排流入，依次流经整个所述第二外排、及所述第二内排的剩余部分，并从所述第二内排流出；所述第三支路从所述第三外排流入，并依次流经整个第三外排和第三内排，并从所述第三内排流出。
  10. 如权利要求9所述的换热器组件，其中，所述第一支路从所述第一外排的靠近所述中换热器的换热管流入，依次流经整个所述第一外排和第一内排，到达所述第一内排的靠近所述中换热器的换热管，再经过所述第一跨接管进入所述第二内排。
  11. 如权利要求1所述的换热器组件，其中，所述前换热器的换热管包括第一外排和第一内排，所述中换热器的换热管包括第二外排和第二内排，所述后换热器的换热管包括第三外排和第三内排，所述第一外排、第二外排以及第三外排均靠近所述主体换热器的迎风侧设置；
    当所述换热器组件制冷时，所述第一支路从所述第二外排流入，沿所述第二外排流动并经第一跨接管进入所述第一外排，并依次流经整个所述第一外排和第一内排，再经第二跨接管进入所述第二内排，并从所述第二内排流出；所述第二支路从所述第二外排流入，依次流经所述第二外排和第二内排的剩余部分，并从所述第二内排流出；所述第三支路从所述第三外排流入，并依次流经整个第三外排和第三内排，并从所述第三内排流出。
  12. 如权利要求1所述的换热器组件，其中，所述背管换热器的换热管管径大于所述主体换热器的换热管管径。
  13. 如权利要求12所述的换热器组件，其中，所述背管换热器安装于所述中换热器的迎风侧。
  14. 如权利要求13所述的换热器组件，其中，所述背管换热器相对所述后换热器靠近所述前换热器设置。
  15. 如权利要求12所述的换热器组件，其中，所述背管换热器的换热管数量为2~4根。
  16. 一种空调室内机，其中，包括换热器组件、以及设置为容置所述换热器组件的机壳；所述换热器组件包括：
    主体换热器，呈半包围状设置；所述主体换热器包括前换热器、中换热器以及后换热器，所述前换热器、中换热器以及后换热器在进风方向上均设置有至少两排换热管，所述中换热器的换热管数量大于所述前换热器和后换热器；以及
    背管换热器，安装于所述主体换热器的迎风侧；其中，
    当所述换热器组件制冷时，所述换热器组件的换热流路经过所述背管换热器后分为第一支路、第二支路以及第三支路，所述第一支路、第二支路以及第三支路均自所述主体换热器迎风侧的换热管朝背风侧的换热管流动；所述第一支路流经所述前换热器的换热管，所述第二支路流经所述中换热器的换热管，所述第三支路流经所述后换热器的换热管，且所述第一支路和第三支路中至少一者还跨经所述中换热器的换热管设置。
  17. 如权利要求16所述的空调室内机，其中，所述机壳沿前后向的宽度尺寸小于800mm，所述机壳沿上下向的高度尺寸小于295mm。
  18. 如权利要求16所述的空调室内机，其中，所述换热器组件设于所述机壳内时，所述后换热器的排布方向与上下方向的夹角范围38°~48°。
  19. 如权利要求16所述的空调室内机，其中，所述换热器组件设于所述机壳内时，所述中换热器和前换热器的排布方向与上下方向的夹角范围45°~55°。
  20. 如权利要求16所述的空调室内机，其中，所述中换热器与后换热器相互靠近的一端互相抵接；或
    所述中换热器与后换热器相互靠近的一端之间存有间隙，所述空调室内机还包括挡风板，所述挡风板跨接于所述中换热器和后换热器相互靠近的一端的迎风侧之间。
PCT/CN2018/108820 2018-09-03 2018-09-29 换热器组件和空调室内机 WO2020047927A1 (zh)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2019546860A JP6858268B2 (ja) 2018-09-03 2018-09-29 熱交換器組立品とエアコン室内機

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
CN201811028543.9 2018-09-03
CN201821443587.3U CN209042727U (zh) 2018-09-03 2018-09-03 换热器组件、空调室内机及空气调节装置
CN201821443587.3 2018-09-03
CN201821444281.X 2018-09-03
CN201811028543.9A CN109269071B (zh) 2018-09-03 2018-09-03 换热器组件和空调室内机
CN201821444281.XU CN209042730U (zh) 2018-09-03 2018-09-03 换热器组件、空调室内机以及空气调节装置

Publications (1)

Publication Number Publication Date
WO2020047927A1 true WO2020047927A1 (zh) 2020-03-12

Family

ID=69722168

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2018/108820 WO2020047927A1 (zh) 2018-09-03 2018-09-29 换热器组件和空调室内机

Country Status (2)

Country Link
JP (1) JP6858268B2 (zh)
WO (1) WO2020047927A1 (zh)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010230208A (ja) * 2009-03-26 2010-10-14 Sharp Corp 空気調和機の室内ユニット
CN103090518A (zh) * 2011-10-31 2013-05-08 珠海格力电器股份有限公司 一种换热器及使用该换热器的壁挂式空调器
CN103134355A (zh) * 2013-03-08 2013-06-05 Tcl空调器(中山)有限公司 超薄型换热器及采用该超薄型换热器的壁挂式空调室内机
CN104848515A (zh) * 2015-04-29 2015-08-19 广东美的制冷设备有限公司 空调换热器及挂壁式空调室内机
CN107830658A (zh) * 2017-11-22 2018-03-23 广东美的制冷设备有限公司 换热器、室内机及空调器
CN107843029A (zh) * 2017-11-22 2018-03-27 广东美的制冷设备有限公司 室内换热器、空调室内机及空调器
JP6400378B2 (ja) * 2014-08-07 2018-10-03 東芝ライフスタイル株式会社 空気調和機

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0868568A (ja) * 1994-08-29 1996-03-12 Toshiba Corp 空気調和機
JP5316668B1 (ja) * 2012-04-16 2013-10-16 ダイキン工業株式会社 空気調和機
JP5772787B2 (ja) * 2012-10-31 2015-09-02 ダイキン工業株式会社 空気熱交換器
JP6639865B2 (ja) * 2015-10-30 2020-02-05 東芝キヤリア株式会社 空気調和装置の室内ユニット
JP2017096588A (ja) * 2015-11-27 2017-06-01 パナソニックＩｐマネジメント株式会社 空気調和機

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010230208A (ja) * 2009-03-26 2010-10-14 Sharp Corp 空気調和機の室内ユニット
CN103090518A (zh) * 2011-10-31 2013-05-08 珠海格力电器股份有限公司 一种换热器及使用该换热器的壁挂式空调器
CN103134355A (zh) * 2013-03-08 2013-06-05 Tcl空调器(中山)有限公司 超薄型换热器及采用该超薄型换热器的壁挂式空调室内机
JP6400378B2 (ja) * 2014-08-07 2018-10-03 東芝ライフスタイル株式会社 空気調和機
CN104848515A (zh) * 2015-04-29 2015-08-19 广东美的制冷设备有限公司 空调换热器及挂壁式空调室内机
CN107830658A (zh) * 2017-11-22 2018-03-23 广东美的制冷设备有限公司 换热器、室内机及空调器
CN107843029A (zh) * 2017-11-22 2018-03-27 广东美的制冷设备有限公司 室内换热器、空调室内机及空调器

Also Published As

Publication number Publication date
JP2020535368A (ja) 2020-12-03
JP6858268B2 (ja) 2021-04-14

Similar Documents

Publication Publication Date Title
WO2018105928A1 (ko) 차량용 열관리 시스템
WO2012169713A1 (en) Air conditioner with a cooling module
WO2021172882A1 (ko) 공기조화장치
WO2010128695A1 (ko) 공기 조화기
CN104638879A (zh) 变频器及空调器
WO2019146832A1 (ko) 공기조화기의 실외기
WO2020103579A1 (zh) 空调室内机和空调器
WO2012162938A1 (zh) 空气换热装置及其制造方法和空气换热空调一体机装置
WO2015142047A1 (en) Outdoor unit of an air conditioner and method of manufacturing the same
EP3322940A1 (en) Air conditioner
WO2020047926A1 (zh) 换热器组件和空调室内机
CN208804767U (zh) 一种多温送风空调系统
WO2018176553A1 (zh) 空调室内机和空调器
CN209749011U (zh) 一种降温装置
CN205079337U (zh) 一种模块化列间空调
WO2020047927A1 (zh) 换热器组件和空调室内机
CN108954537A (zh) 一种多温送风空调系统
CN215490076U (zh) 一种多用途热泵除湿系统及机构
WO2019080787A1 (zh) 空调室内机的换热器组件及空调室内机
WO2019027085A1 (ko) 공기열원 축냉운전과 수열원 축냉축열 동시운전을 갖는 다중열원 멀티 히트펌프 시스템 및 제어방법
CN201476645U (zh) 一种隔离式逆流空气换热装置
WO2018176554A1 (zh) 空调室内机和空调器
WO2018058744A1 (zh) 空调挂机
WO2020047928A1 (zh) 壁挂式空调室内机及壁挂式空调器
CN216852850U (zh) 空气调节模块以及电控柜

Legal Events

Date Code Title Description
ENP Entry into the national phase

Ref document number: 2019546860

Country of ref document: JP

Kind code of ref document: A

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18932676

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

32PN Ep: public notification in the ep bulletin as address of the adressee cannot be established

Free format text: NOTING OF LOSS OF RIGHTS PURSUANT TO RULE 112(1) EPC (EPO FORM 1205A DATED 06/08/2021

122 Ep: pct application non-entry in european phase

Ref document number: 18932676

Country of ref document: EP

Kind code of ref document: A1