Heat exchanger and air conditioner with same

Abstract

The invention provides a heat exchanger and an air conditioner with the heat exchanger. The heat exchanger comprises a heat exchange piece and a first collecting pipe. The heat exchange part is provided with a plurality of heat exchange flat pipes, the heat exchange flat pipes are connected with the first flow collecting pipe, the first flow collecting pipe is provided with a first flow channel in the axial direction of the first flow collecting pipe, and the heat exchange flat pipes communicate with the first flow channel; the first collecting pipe comprises a first end and a second end, the two ends of the first flow channel communicate with the first end and the second end correspondingly, the first end is provided with an inlet and outlet, a first rotational flow piece is arranged at the inlet and outlet, and a second rotational flow piece is arranged at the second end. The first rotational flow part is arranged at the inlet and outlet, and the second rotational flow part is arranged at the second end, so that a refrigerant flows into the collecting pipe in a spiral shape, the influence of the gravity factor is weakened by utilizing centrifugal force generated by rotation, and uniform flow division is completed.

Description

Technical Field

[0001] The present invention belongs to the technical field of air conditioners, and in particular relates to a heat exchanger and an air conditioner having the heat exchanger. Background Art

[0002] Air conditioning provides a strong guarantee for a comfortable living environment. Its heat exchangers mainly include finned tube heat exchangers and microchannel heat exchangers. Compared with finned tube heat exchangers, microchannel heat exchangers can effectively reduce the amount of refrigerant injection and improve economic efficiency. They are widely concerned by enterprises and are being researched and developed. Microchannel heat exchangers have many branches, and the manifolds and microchannel flat tubes have resistance. When the heat exchanger is used as an evaporator, the liquid distributor has the problem of uneven flow distribution when distributing the microchannel flat tubes, which directly affects the heat exchange efficiency of the heat exchanger, resulting in increased power consumption, reduced economic efficiency and comfort. The refrigerant needs to be evenly distributed to each flat tube at the inlet.

[0003] The related art discloses a flow uniform distribution device, including a number of descending branches, a first diversion chamber and a second diversion chamber connected in sequence, the ascending pipe, the descending branch, the first diversion chamber and the second diversion chamber are arranged in sequence from the inside to the outside, and the several descending branches are distributed along the circumference of the ascending pipe. The application of this flow uniform distribution device can give full play to the heat transfer potential of the heat exchanger and improve the efficiency of the heat exchanger. However, the structure is complex and not conducive to processing. The related art discloses a microchannel heat exchanger, which uses a diverter to divide the total flow path into 4 paths, and the flat tubes of the heat exchanger are divided into 4 areas according to different proportions. The manifold in each area corresponds to a refrigerant branch, and the refrigerant on each branch is distributed to the flat tube through the injection partition. The problem of uneven refrigerant diversion in the microchannel heat exchanger in the air conditioner of the upper air outlet type in the prior art is solved, but the manifold has too many internal partitions and the injection holes with complex structure will still have the problem of uneven injection. Summary of the invention

[0004] The present invention provides a heat exchanger and an air conditioner having the heat exchanger, which can solve the technical problem that when the heat exchanger is used as an evaporator, the refrigerant in the header is unevenly distributed to each microchannel flat tube during flow division.

[0005] The present invention provides a heat exchanger, which includes a heat exchange element, a first header, a first cyclone element, and a second cyclone element;

[0006] The heat exchange element comprises a plurality of heat exchange flat tubes, the plurality of heat exchange flat tubes are respectively connected to the first header, along the axial direction of the first header, the first header comprises a first flow channel, the plurality of heat exchange flat tubes are respectively connected to the first flow channel;

[0007] The first collecting pipe includes a first end and a second end. Both ends of the first flow channel are respectively connected to the first end and the second end. The first end has an inlet and an outlet, and a first swirl component is arranged at the inlet and outlet. The second end is provided with a second swirl component.

[0008] In some embodiments, a plurality of the heat exchange flat tubes are arranged side by side, and a notch is provided at one end of the plurality of heat exchange flat tubes connected to the first collecting pipe, and the plurality of notches have at least a first shape and a second shape, and the notches of the first shape and the notches of the second shape are arranged alternately.

[0009] In some embodiments, the first collecting pipe includes a tube body and a shunt tube, the tube body has the first flow channel, the shunt tube is arranged on the outer wall of the tube body, two ends of the shunt tube extend to two ends of the tube body respectively, and along the axial direction of the shunt tube, the shunt tube has a second flow channel, and one end of the second flow channel close to the second end is connected to the first flow channel.

[0010] In some embodiments, the first swirl member includes a first cover body and a first swirl blade, one end of the first cover body is connected to the first end, the other end of the first cover body is a diversion port, the first flow channel and the second flow channel are both connected to the first cover body, and the first swirl blade is arranged in the first cover body.

[0011] In some embodiments, the first cover body includes a first diverter chamber and a second diverter chamber, one end of the first diverter chamber is connected to the first flow channel, the other end of the first diverter chamber is connected to the diverter port, and the first swirl blade is arranged in the first diverter chamber; one end of the second diverter chamber is connected to the second flow channel, and the other end of the second diverter chamber is connected to the diverter port.

[0012] In some embodiments, the diversion port is provided with a liquid separation component, which includes a first branch pipe, a second branch pipe and a diverter, one end of the first branch pipe and the second branch pipe are connected to the first cover body, and the first branch pipe is connected to the first diversion cavity, and the second branch pipe is connected to the second diversion cavity; the other ends of the first branch pipe and the second branch pipe are connected to the diverter.

[0013] In some embodiments, the refrigerant flow rate in the shunt pipe is greater than the refrigerant flow rate in the pipe body, and the cross-sectional area of ​​the second flow channel is smaller than the cross-sectional area of ​​the first flow channel.

[0014] In some embodiments, the second swirl member includes a second cover body and a second swirl blade, one end of the second cover body is connected to the second end, the other end of the second cover body is sealed, the second swirl blade is arranged in the second cover body, and the first flow channel and the second flow channel are both connected to the second cover body.

[0015] In some embodiments, a partition plate is provided in the second cover body, and the partition plate divides the inner cavity of the second cover body into a first chamber and a second chamber, the first chamber is connected to the first flow channel, the second swirl blade is arranged in the first chamber, and the second chamber is connected to the second flow channel, and a connecting hole for connecting the first chamber and the second chamber is provided on the partition plate.

[0016] An air conditioner comprises a heat exchanger, wherein the heat exchanger is the above-mentioned heat exchanger.

[0017] A heat exchanger and an air conditioner having the heat exchanger provided by the present invention have the following beneficial effects:

[0018] When the air conditioner is running in cooling mode and the heat exchanger is used as a condenser, the high-temperature and high-pressure gaseous refrigerant from the compressor exhaust port first flows into the second header and is divided in the second header. The gaseous refrigerant enters multiple heat exchange flat tubes respectively. At this time, the gaseous refrigerant in the microchannel heat exchange flat tube has begun to exchange heat with the outside and condense. The liquid refrigerant that has completed condensation in all microchannel heat exchange flat tubes enters the first header, gathers together in the first flow channel, and then flows out from the inlet and outlet.

[0019] When the air conditioner is running in heating mode and the heat exchanger is used as an evaporator, the flow direction of the entire refrigerant is opposite to that when the heat exchanger is used as a condenser. The first header is the main distribution component of the heat exchanger, responsible for evenly distributing the refrigerant to each heat exchange flat tube. The throttled gas-liquid two-phase refrigerant first flows in from the inlet and outlet, and then flows through the first swirl component. The rotating refrigerant flows in the first flow channel in the first header. The first flow channel is connected to the heat exchange flat tube, so that the refrigerant can be evenly distributed to each heat exchange flat tube and distributed to each heat exchange flat tube for evaporation and heat exchange. As the refrigerant flows in the first flow channel, the refrigerant flowing to the second end will flow through the second swirl component and enter the heat exchange flat tube for evaporation and heat exchange. After completing evaporation and heat exchange, the gaseous refrigerant gathers in the second header and then enters the next process.

[0020] The present invention is provided with a first swirl component at the inlet and outlet, and a second swirl component at the second end, so that the refrigerant flow trajectory is spirally entered into the manifold, and the centrifugal force generated by the rotation is used to distribute the refrigerant to each microchannel flat tube under the action of the centrifugal force of the liquid particles of different sizes in the first flow channel, thereby weakening the influence of the gravity factor and completing the uniform flow distribution. The swirl component helps to improve the mixing effect of the refrigerant in the first manifold by causing the refrigerant to produce a rotating flow. This rotating flow can break up the eddy currents and dead zones in the refrigerant, ensuring that the refrigerant is more evenly distributed to each heat exchange flat tube. In the heating mode, the throttled gas-liquid two-phase refrigerant can enter the heat exchange flat tube more evenly for evaporation and heat exchange through the rotating action of the swirl component. In addition, the provision of the first swirl component and the second swirl component can reduce the resistance in the flow of the gas-liquid two-phase refrigerant, so that the refrigerant passes through the first manifold and the heat exchange flat tube more smoothly. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to more clearly illustrate the implementation methods of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for the implementation methods or the description of the prior art. Obviously, the drawings in the following description are only exemplary, and for ordinary technicians in this field, other implementation drawings can be derived from the provided drawings without creative work.

[0022] Figure 1 is a schematic diagram of a heat exchanger according to an embodiment of the present invention;

[0023] Figure 2 is a schematic diagram of a first header according to an embodiment of the present invention;

[0024] Figure 3 is a cross-sectional view of a first header according to an embodiment of the present invention;

[0025] Figure 4 Schematic diagram of notches of first to third shapes according to an embodiment of the present invention;

[0026] Figure 5 is a schematic diagram of a second cyclone member and a first header according to an embodiment of the present invention;

[0027] Figure 6 is a schematic diagram of a first swirl member according to an embodiment of the present invention;

[0028] Figure 7 is a schematic diagram of a first shell according to an embodiment of the present invention;

[0029] Figure 8 A schematic diagram of a first diversion cavity and a second diversion cavity according to an embodiment of the present invention;

[0030] Fig. 9 is an exploded view of a second swirl member according to an embodiment of the present invention;

[0031] Fig.10 is a schematic diagram of a second swirl member according to an embodiment of the present invention;

[0032] Fig.11 is a schematic diagram of a second housing according to an embodiment of the present invention;

[0033] Fig.12 Schematic diagram of a second header according to an embodiment of the present invention.

[0034] Figures: 1-heat exchange element; 101-heat exchange flat tube; 102-notch; 121-first shape; 122-second shape; 123-third shape; 2-first collecting pipe; 21-first end; 22-second end; 201-first flow channel; 202-inlet and outlet; 203-tube body; 204-diverter; 205-second flow channel; 3-first swirl element; 301-first cover body; 311-first diverter cavity; 312-second diverter cavity; 302-first swirl blade; 303-diverter port; 4-second swirl element; 401-second cover body; 402-second swirl blade; 403-partition plate; 431-first chamber; 432-second chamber; 433-connecting hole; 5-liquid separation component; 501-first branch pipe; 502-second branch pipe; 503-diverter; 6-second collecting pipe. DETAILED DESCRIPTION

[0035] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, rather than all the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means intended to limit the present invention and its application or use. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0036] In the description of the present invention, it is necessary to understand that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "lateral, vertical, perpendicular, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the drawings. They are only for the convenience of describing the present invention and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the devices or elements referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of the present invention. The directional words "inside and outside" refer to the inside and outside relative to the contours of each component itself.

[0037] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used here to describe the spatial positional relationship between a device or feature and other devices or features as shown in the figure. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figure. For example, if the device in the accompanying drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0038] In addition, it should be noted that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. If not otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of the present invention.

[0039] See also Figure 1 and Figure 2 As shown, according to an embodiment of the present invention, a heat exchanger is provided, which includes a heat exchange element, a first header 2, a first swirl element 3 and a second swirl element 4; the heat exchange element has a plurality of heat exchange flat tubes 101, and the plurality of heat exchange flat tubes 101 are respectively connected to the first header 2, and along the axial direction of the first header 2, the first header 2 has a first flow channel 201, and the plurality of heat exchange flat tubes 101 are respectively connected to the first flow channel 201; the first header 2 includes a first end 21 and a second end 22, and the two ends of the first flow channel 201 are respectively connected to the first end 21 and the second end 22, and the first end 21 has an inlet and outlet 202, and the first swirl element 3 is arranged at the inlet and outlet 202, and the second end 22 is arranged at the second swirl element 4.

[0040] As a specific implementation, one end of the plurality of heat exchange flat tubes 101 is connected to the first header 2, and the other end of the plurality of heat exchange flat tubes 101 is connected to the second header 6. The heat exchange flat tubes 101 are microchannel heat exchange flat tubes.

[0041] Specifically, when the air conditioner is in cooling mode and the heat exchanger is used as a condenser, the high-temperature and high-pressure gaseous refrigerant from the compressor exhaust port first flows into the second header 6, and is divided in the second header 6. The gaseous refrigerant enters the plurality of heat exchange flat tubes 101 respectively. At this time, the gaseous refrigerant in the microchannel heat exchange flat tubes 101 has begun to exchange heat with the outside and condense. The liquid refrigerant that has completed condensation in all microchannel heat exchange flat tubes 101 enters the first header 2, gathers together in the first channel, and then flows out from the inlet and outlet 202.

[0042] Specifically, when the air conditioner is running in heating mode and the heat exchanger is used as an evaporator, the flow direction of the entire refrigerant is opposite to the flow direction when the heat exchanger is used as a condenser. The first header 2 is the main distribution component of the heat exchanger, responsible for evenly distributing the refrigerant to each heat exchange flat tube 101. The throttled gas-liquid two-phase refrigerant first flows in from the inlet and outlet 202, and then flows through the first swirl component 3. The rotating refrigerant flows in the first flow channel 201 in the first header 2. The first flow channel 201 is connected to the heat exchange flat tube 101, so that the refrigerant can be evenly distributed to each heat exchange flat tube 101 and distributed to each heat exchange flat tube 101 for evaporation and heat exchange. As the refrigerant flows in the first flow channel 201, the refrigerant flowing to the second end 22 will flow through the second swirl component 4 and then enter the heat exchange flat tube 101 for evaporation and heat exchange. After completing evaporation and heat exchange, the gaseous refrigerant gathers in the second header 6 and then enters the next process.

[0043] In this embodiment, a first swirl component 3 is provided at the inlet and outlet 202, and a second swirl component 4 is provided at the second end 22, so that the refrigerant flow trajectory is spirally entered into the header, and the centrifugal force generated by the rotation is used to distribute the refrigerant to each microchannel flat tube under the action of the centrifugal force of the liquid particles of different sizes in the first flow channel 201, thereby weakening the influence of the gravity factor and completing the uniform flow distribution. The swirl component helps to improve the mixing effect of the refrigerant in the first header 2 by causing the refrigerant to produce a rotating flow. This rotating flow can break up the eddy current and dead zone in the refrigerant, ensuring that the refrigerant is more evenly distributed to each heat exchange flat tube 101. In the heating mode, the throttled gas-liquid two-phase refrigerant can also enter the heat exchange flat tube 101 more evenly for evaporation and heat exchange through the rotating action of the swirl component. In addition, the provision of the first swirl component 3 and the second swirl component 4 can reduce the resistance in the flow of the gas-liquid two-phase refrigerant, so that the refrigerant passes through the first header 2 and the heat exchange flat tube 101 more smoothly.

[0044] See also Figures 1 to 8As shown, the heat exchange flat tubes 101 are arranged side by side, and one end of the heat exchange flat tubes 101 connected to the first collecting pipe 2 is provided with a notch 102, and the plurality of notches 102 have at least a first shape 121 and a second shape 122, and the notches 102 of the first shape 121 and the notches 102 of the second shape 122 are arranged alternately.

[0045] In this embodiment, the gas-liquid two-phase refrigerant first flows from the inlet and outlet 202, flows into the first flow channel 201, and flows into the corresponding heat exchange flat tube 101 from each notch 102. The state of the refrigerant here is gas-liquid two-phase flow. After the first swirl component 3 and the second swirl component 4 turbulence, droplets of different volumes will be formed. The flow velocities of these droplets will be different, and the centrifugal forces will be different, so the movement radius in the plane will be different. Since the notch 102 has at least two shapes, the curved surface of the notch 102 with different radii can accept droplets of various movement radii, so that droplets subjected to different centrifugal forces can all enter the microchannel heat exchange flat tube 101. In addition, in the multi-path parallel heat exchange flat tube 101, the first swirl component 3 and the second swirl component 4 can prevent the refrigerant from tending to flow along a certain path and ignoring other paths, ensuring that each heat exchange flat tube 101 can obtain an appropriate amount of refrigerant to avoid local overheating or overcooling.

[0046] As a specific implementation, in the axial direction of the heat exchanger 1, the lengths of the heat exchange flat tubes 101 are the same, that is, the ends of the heat exchange flat tubes 101 connected to the second manifold 6 are coplanar, and the other ends of the heat exchange flat tubes 101 are provided with notches 102 of different shapes, and the cross-sections of the notches 102 can be arc-shaped, the first shape 121 is an arc with a smaller arc, and the second shape 122 is an arc with a larger arc. Three or more arcs with increasing arcs can also be provided, so that droplets subjected to different centrifugal forces can all enter the microchannel variable tube. For example, the first heat exchange flat tube 101 is a first shape 121, the second heat exchange flat tube 101 is a second shape 122, and the third heat exchange flat tube 101 is a third shape 123. The curvatures of the first shape 121 to the third shape 123 gradually increase. The first heat exchange flat tube 101 to the third heat exchange flat tube 101 are arranged in sequence, and the first heat exchange flat tube 101 to the third heat exchange flat tube 101 are repeatedly arranged from top to bottom or from bottom to top. In other embodiments, the first heat exchange flat tube 101 to the third heat exchange flat tube 101 can also be arranged at irregular staggered intervals.

[0047] See also Figures 2 to 5As shown, the first collecting pipe 2 includes a tube body 203 and a diverter pipe 204, the tube body 203 has a first flow channel 201, the diverter pipe 204 is arranged on the outer wall of the tube body 203, and the two ends of the diverter pipe 204 extend to the two ends of the tube body 203 respectively. Along the axial direction of the diverter pipe 204, the diverter pipe 204 has a second flow channel 205, and the end of the second flow channel 205 close to the second end 22 is connected to the first flow channel 201.

[0048] Specifically, when the air conditioner is running in heating mode and the heat exchanger is used as an evaporator, the flow direction of the entire refrigerant is opposite to that when the heat exchanger is used as a condenser. The throttled gas-liquid two-phase refrigerant first flows through the first swirl component 3, and then flows into the first flow channel 201 and the second flow channel 205 respectively. The gas-liquid two-phase refrigerant in the first flow channel 201 is respectively distributed to the heat exchange flat tube 101; the gas-liquid two-phase refrigerant in the second flow channel 205 first flows from bottom to top, and after the gas-liquid two-phase refrigerant flows to the second end 22, since the second end is provided with a second swirl component 4, the gas-liquid two-phase refrigerant first flows through the second swirl component 4 and then flows into the first flow channel 201. The refrigerant entering the first flow channel 201 flows from top to bottom and then is distributed to the heat exchange flat tube 101.

[0049] In this embodiment, the state of the refrigerant here is a gas-liquid two-phase flow. After flowing out of the first swirl component 3, the refrigerant is divided into two paths and flows into the first flow channel 201 and the second flow channel 205 respectively. At the inlet and outlet 202, the refrigerant will undergo a swirl under the action of the first swirl component 3, and the influence of gravity factors will be weakened by the rotating centrifugal force generated by the swirl. If the refrigerant flows into the first flow channel 201 from the first end 21, and the swirl will reduce the speed in the vertical direction, it will cause uneven flow distribution of the flat tube at the top. This embodiment fully combines the swirl effect of the first swirl component 3 and the second swirl component 4 and the shunting effect of the shunt pipe 204, which can reduce the resistance in the flow of the refrigerant, so that the refrigerant can pass through the first manifold 2 and the heat exchange flat tube 101 more smoothly, reduce the pressure loss of the system, and through the cooperation of the shunt pipe 204 and the second swirl component 4, it can ensure that the flow of the refrigerant in the heat exchanger is more uniform, and improve the heat exchange efficiency and uniformity of the entire heat exchanger.

[0050] In addition, when the ends of the heat exchange flat tubes 101 connected to the first collecting pipe 2 are each provided with a notch 102, and the plurality of notches 102 have at least a first shape 121 and a second shape 122, and the notches 102 of the first shape 121 and the notches 102 of the second shape 122 are arranged alternately, the gas-liquid two-phase refrigerant first flows through the first vortex 3, and then flows into the first flow channel 201 and the second flow channel 205 respectively, and the refrigerant in the second flow channel 205 will also flow through the second vortex component 4, so that the refrigerant flow trajectory presents a spiral shape and enters the first collecting pipe 2. The centrifugal force generated by the rotation is used to fit the flat tubes with notches of different curvatures at the ends, and the refrigerant is distributed to each microchannel flat tube to complete uniform diversion.

[0051] See also Figures 1 to 8 As shown, the first swirl member 3 includes a first cover body 301 and a first swirl blade 302, one end of the first cover body 301 is connected to the first end 21, the other end of the first cover body 301 is a diversion port 303, the first flow channel 201 and the second flow channel 205 are both connected to the first cover body 301, and the first swirl blade 302 is arranged in the first cover body 301.

[0052] Specifically, the throttled gas-liquid two-phase refrigerant first flows into the first cover body 301 from the diversion port 303, and then flows into the first flow channel 201 and the second flow channel 205 respectively after passing through the first swirl blade 302. The gas-liquid two-phase refrigerant in the first flow channel 201 is respectively distributed to the heat exchange flat tubes 101; the gas-liquid two-phase refrigerant in the second flow channel 205 first flows from bottom to top, and then flows to the second end 22, first flows through the second swirl component 4 and then flows into the first flow channel 201. The refrigerant entering the first flow channel 201 flows from top to bottom and then is distributed to the heat exchange flat tubes 101.

[0053] In this embodiment, the first swirl blades 302 cause the refrigerant to generate a rotating flow in the first cover body 301, which helps to break up the vortex and dead zones in the refrigerant, thereby ensuring that the refrigerant is more evenly distributed to each heat exchange flat tube 101. The first swirl blades 302 can also reduce the resistance during the flow of the refrigerant, allowing the refrigerant to pass through the first collecting pipe 2 more smoothly. In addition, the first swirl blades 302 can use centrifugal force to distribute droplets of different sizes to each heat exchange flat tube 101, weaken the influence of gravity factors, and achieve uniform diversion.

[0054] See also Figures 1 to 8 As shown, the first cover body 301 includes a first diverter chamber 311 and a second diverter chamber 312, one end of the first diverter chamber 311 is connected to the first flow channel 201, and the other end of the first diverter chamber 311 is connected to the diverter port 303, and the first swirl blade 302 is arranged in the first diverter chamber 311; one end of the second diverter chamber 312 is connected to the second flow channel 205, and the other end of the second diverter chamber 312 is connected to the diverter port 303.

[0055] In this embodiment, the refrigerant flowing into the first cover body 301 from the diverter port 303 will flow into the first diverter cavity 311 and the second diverter cavity 312 respectively, and then flow into the first flow channel 201 and the second flow channel 205 respectively. In this embodiment, since the refrigerant in the first flow channel 201 will be first distributed to the heat exchange flat tube 101, the first swirl blade 302 is arranged in the first diverter cavity 311, and the refrigerant flows from the diverter port 303 and flows through the first swirl blade 302, and then flows from the first diverter cavity 311 into the first flow channel 201. The refrigerant in the second diverter cavity 312 flows into the second flow channel 205, flows to the second end 22, flows through the second swirl member 4, and then flows into the first flow channel 201. It is worth noting that in this embodiment, it is preferred that the first swirl blade 302 is arranged in the first diverter cavity 311, and in other embodiments, a swirl blade can also be arranged in the second diverter cavity 312.

[0056] In this embodiment, the provision of the first flow diversion chamber 311 and the second flow diversion chamber 312 helps to distribute the refrigerant more evenly to each flow channel. This distribution method can reduce the local accumulation of refrigerant in some areas, thereby improving the heat exchange efficiency. The first cover 301 integrates the flow diversion chamber and the swirl blades together, making the structure of the heat exchanger more compact and saving space. In addition, the provision of the flow diversion chamber makes the flow of the refrigerant in the first manifold 2 more orderly.

[0057] As a specific implementation, the first diversion chamber 311 is a gradually converging and expanding structure along the flow direction of the refrigerant, and the second diversion chamber 312 is a gradually expanding and converging structure along the flow direction of the refrigerant. This arrangement takes into account the larger space for installing the first swirl blade 302. The first diversion chamber 311 can provide a larger space for this structure, and the structure of the second diversion chamber 312 is adaptively deformed.

[0058] See also Figures 1 to 8 As shown, the diversion port 303 is provided with a liquid separation component 5, and the liquid separation component 5 includes a first branch pipe 501, a second branch pipe 502 and a diverter 503. One end of the first branch pipe 501 and the second branch pipe 502 are connected to the first cover body 301, and the first branch pipe 501 is connected to the first diversion chamber 311, and the second branch pipe 502 is connected to the second diversion chamber 312; the other ends of the first branch pipe 501 and the second branch pipe 502 are connected to the diverter 503.

[0059] Specifically, before the gas-liquid two-phase refrigerant flows in from the diversion port 303, the refrigerant discharged from the compressor first flows into the diverter 503 for turbulence. At this time, the refrigerant gas and liquid have been evenly mixed after the turbulence, and then distributed to the first branch pipe 501 and the second branch pipe 502; the first branch pipe 501 and the second branch pipe 502 respectively guide the refrigerant to the first diversion chamber 311 and the second diversion chamber 312.

[0060] In this embodiment, the design of the liquid separation component 5 ensures that the refrigerant can be evenly distributed to the first diversion chamber 311 and the second diversion chamber 312. The refrigerant is divided into two paths, which can be more evenly distributed than using one path alone. The centrifugal force generated by the rotation is then used. Liquid particles of different sizes in the fluid are radially arranged on the cross section of the tube body 203 under the action of centrifugal force. The droplets fit the heat exchange flat tubes 101 with different curvature notches at the ends, and the refrigerant is distributed to each microchannel flat tube to complete uniform diversion, which helps to improve the uniformity of the flow of the refrigerant in the heat exchanger, thereby improving the heat exchange efficiency and uniformity of the entire heat exchanger. It can also prevent the refrigerant from tending to flow along a certain path and ignoring other paths, ensuring that each heat exchange flat tube 101 can obtain an appropriate amount of refrigerant.

[0061] See also Figures 1 to 8 As shown, the refrigerant flow rate in the shunt pipe 204 is greater than the refrigerant flow rate in the pipe body 203 , and the cross-sectional area of ​​the second flow channel 205 is smaller than the cross-sectional area of ​​the first flow channel 201 .

[0062] In this embodiment, since the first swirl blade 302 is provided in the first diversion chamber 311, and the refrigerant flowing into the second flow channel 205 needs to flow from bottom to top first, the refrigerant flow path in the second flow channel 205 is longer. If the amount of refrigerant in the second flow channel 205 is larger and the cross-sectional area of ​​the second flow channel 205 is smaller, the refrigerant flow rate in the second flow channel 205 is faster, and the refrigerant in the second flow channel 205 is easier to flow to the second end 22. The refrigerant flowing to the second end 22 will first flow through the second swirl component 4, and then flow into the first flow channel 201. This specific flow rate and flow channel cross-sectional area setting helps to optimize the performance of the heat exchanger, improve the heat exchange efficiency and the overall performance of the system.

[0063] As a specific implementation, since the first branch pipe 501 and the second branch pipe 502 are respectively connected to the first diversion chamber 311 and the second diversion chamber 312, the diameter of the second branch pipe 502 is set to be larger than the diameter of the first branch pipe 501 to ensure that more refrigerant flows into the second diversion chamber 312, thereby increasing the amount of refrigerant in the second flow channel 205.

[0064] See also Figures 1 to 8 As shown, the second swirl member 4 includes a second cover body 401 and a second swirl blade 402, one end of the second cover body 401 is connected to the second end 22, the other end of the second cover body 401 is sealed, the second swirl blade 402 is arranged in the second cover body 401, and the first flow channel 201 and the second flow channel 205 are both connected to the second cover body 401.

[0065] Specifically, the gas-liquid two-phase refrigerant in the second flow channel 205 first flows from bottom to top. After flowing to the second end 22, the gas-liquid two-phase refrigerant first flows into the second cover body 401, flows through the second swirl blade 402, and then flows into the first flow channel 201. The refrigerant entering the first flow channel 201 flows from top to bottom and is then distributed to the heat exchange flat tube 101.

[0066] In this embodiment, the second swirl blade 402 causes the refrigerant to generate a rotating flow in the second cover 401, so that the refrigerant in the second flow channel 205 flows into the first flow channel 201. This swirl effect helps to enhance the disturbance and mixing of the refrigerant, thereby improving the heat exchange efficiency. The second swirl blade 402 can use centrifugal force to distribute droplets of different sizes to each heat exchange flat tube 101, weaken the influence of gravity factors, and complete uniform flow distribution. The second swirl member 4 integrates the swirl blade in the second cover 401, making the structure of the heat exchanger more compact and saving space.

[0067] See also Figures 1 to 8 As shown, a partition plate 403 is provided in the second cover body 401, and the partition plate 403 divides the inner cavity of the second cover body 401 into a first chamber 431 and a second chamber 432. The first chamber 431 is connected to the first flow channel 201, and the second swirl blade 402 is arranged in the first chamber 431. The second chamber 432 is connected to the second flow channel 205, and a connecting hole 433 for connecting the first chamber 431 and the second chamber 432 is provided on the partition plate 403.

[0068] In this embodiment, the refrigerant flow in the shunt pipe 204 is greater than the refrigerant flow in the tube body 203, and the cross-sectional area of ​​the second flow channel 205 is greater than the cross-sectional area of ​​the first flow channel 201, so that the refrigerant flow rate in the second flow channel 205 is faster, and the refrigerant flows to the connecting hole 433 and then flows through the second swirl blade 402, and the swirled refrigerant flows into the first flow channel 201. The partition plate 403 divides the chamber of the second cover body 401 to prevent the refrigerants in the two flow channels from mixing without passing through the second swirl blade 402.

[0069] As a specific implementation manner, the first swirl blade 302 and the second swirl blade 402 include a connecting shaft and a spiral blade, and the spiral blade is installed on the connecting shaft. In this embodiment, the length of the first swirl blade 302 and the second swirl blade 402 is relatively short. In other embodiments, the length can be extended as needed, or multiple swirl blades can be set in the middle of the first collecting pipe 2, or swirl blades can be set at both ends of the diverter pipe 204 or in the middle of the diverter pipe 204.

[0070] As a specific implementation manner, mounting holes for connecting with the heat exchange flat tubes 101 are respectively provided on the sides of the first header 2 and the second header 6 .

[0071] As a specific embodiment, the structure of the first collecting pipe 1 includes a tube body 203 and a diverter pipe 204, the tube body 203 has a first flow channel 201, the diverter pipe 204 is arranged on the outer wall of the tube body 203, and the two ends of the diverter pipe 204 extend to the two ends of the tube body 203 respectively. Along the axial direction of the diverter pipe 204, the diverter pipe 204 has a second flow channel 205, and the end of the second flow channel 205 close to the second end 22 is connected to the first flow channel 201. The first swirl member 3 includes a first cover body 301 and a first swirl blade 302, one end of the first cover body 301 is connected to the first end 21, the other end of the first cover body 301 is a diversion port 303, the first flow channel 201 and the second flow channel 205 are both connected to the first cover body 301, and the first swirl blade 302 is arranged in the first cover body 301; the first cover body 301 includes a first diversion chamber 311 and a second diversion chamber 312, and the diversion port 303 is provided with a liquid separation component 5, the liquid separation component 5 includes a first branch pipe 501, a second branch pipe 502 and a diverter 503, one end of the first branch pipe 501 and the second branch pipe 502 are both connected to the first cover body 301, and the first branch pipe 501 is connected to the first diversion chamber 311, and the second branch pipe 502 is connected to the second diversion chamber 312; the other ends of the first branch pipe 501 and the second branch pipe 502 are both connected to the diverter 503. The second swirl member 4 includes a second cover body 401 and a second swirl blade 402 . One end of the second cover body 401 is connected to the second end 22 . The other end of the second cover body 401 is sealed. The second swirl blade 402 is arranged in the second cover body 401 . The first flow channel 201 and the second flow channel 205 are both connected to the second cover body 401 .

[0072] Specifically, when the air conditioner is running in heating mode and the heat exchanger is used as an evaporator, the flow direction of the entire refrigerant is opposite to that when the heat exchanger is used as a condenser. The gas-liquid two-phase refrigerant after throttling first flows through the liquid separation component 5, and the refrigerant after turbulence flows into the first branch pipe 501 and the second branch pipe 502 respectively. One of the refrigerants flows through the first branch cavity 311 in sequence, flows into the first flow channel 201 after being turbulent by the first swirl blade 302, and finally is evenly distributed to multiple heat exchange flat tubes 101; the other refrigerant flows into the second branch cavity 312 and the second flow channel 205 in sequence. After the refrigerant in the second flow channel 205 flows to the second end 22, it flows through the second swirl blade 402 through the connecting hole 433, and then flows into the first flow channel 21. The refrigerant is then distributed to each heat exchange flat tube 101 from top to bottom.

[0073] In this embodiment, the refrigerant flowing out of the first vortex component 3 is divided into two paths and flows into the first flow channel 201 and the second flow channel 205 respectively. At the inlet and outlet 202, the refrigerant will swirl under the action of the first vortex component 3, and the rotational centrifugal force generated by the swirl is used to weaken the influence of gravity. If the refrigerant flows into the first flow channel 201 from the first end 21, and the swirl reduces the speed in the vertical direction, it will cause uneven flow distribution of the flat tubes at the top. This embodiment fully combines the swirl effect of the first vortex component 3 and the second vortex component 4 and the shunting effect of the shunt pipe 204, which can reduce the resistance of the refrigerant flow process, so that the refrigerant can pass through the first manifold 2 and the heat exchange flat tube 101 more smoothly, reduce the pressure loss of the system, and through the cooperation of the shunt pipe 204 and the second vortex component 4, it can ensure that the refrigerant flows more evenly in the heat exchanger, and improve the heat exchange efficiency and uniformity of the entire heat exchanger.

[0074] An air conditioner comprises a heat exchanger, wherein the heat exchanger is the above-mentioned heat exchanger.

[0075] It is easy for those skilled in the art to understand that the above-mentioned advantageous methods can be freely combined and superimposed without conflict.

[0076] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention shall be included in the protection scope of the present invention. The above are only preferred embodiments of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and variations can be made without departing from the technical principles of the present invention, and these improvements and variations should also be regarded as the protection scope of the present invention.

Claims

1. A heat exchanger, characterized in that: include: A heat exchange element (1), a first header (2), a first cyclone element (3) and a second cyclone element (4); The heat exchange element (1) has a plurality of heat exchange flat tubes (101), the plurality of heat exchange flat tubes (101) are respectively connected to the first header (2), along the axial direction of the first header (2), the first header (2) has a first flow channel (201), and the plurality of heat exchange flat tubes (101) are respectively connected to the first flow channel (201); The first collecting pipe (2) comprises a first end (21) and a second end (22); the two ends of the first flow channel (201) are respectively connected to the first end (21) and the second end (22); the first end (21) has an inlet and outlet (202); the first swirl component (3) is arranged at the inlet and outlet (202); and the second end (22) is provided with the second swirl component (4).

2. The heat exchanger according to claim 1, characterized in that: A plurality of the heat exchange flat tubes (101) are arranged side by side, and a notch (102) is provided at one end of the plurality of heat exchange flat tubes (101) connected to the first collecting pipe (2). The plurality of notches (102) have at least a first shape (121) and a second shape (122), and the notches (102) of the first shape (121) and the notches (102) of the second shape (122) are arranged alternately.

3. The heat exchanger according to claim 1, characterized in that: The first collecting pipe (2) comprises a pipe body (203) and a flow dividing pipe (204); the pipe body (203) has the first flow channel (201); the flow dividing pipe (204) is arranged on the outer wall of the pipe body (203); two ends of the flow dividing pipe (204) respectively extend toward two ends of the pipe body (203); along the axial direction of the flow dividing pipe (204), the flow dividing pipe (204) has a second flow channel (205); an end of the second flow channel (205) close to the second end (22) is connected to the first flow channel (201).

4. The heat exchanger according to claim 3, characterized in that The first swirl member (3) comprises a first cover body (301) and a first swirl blade (302); one end of the first cover body (301) is connected to the first end (21); the other end of the first cover body (301) is a diversion port (303); the first flow channel (201) and the second flow channel (205) are both connected to the first cover body (301); and the first swirl blade (302) is arranged in the first cover body (301).

5. The heat exchanger according to claim 4, characterized in that: The first cover body (301) comprises a first diverter chamber (311) and a second diverter chamber (312); one end of the first diverter chamber (311) is connected to the first flow channel (201), and the other end of the first diverter chamber (311) is connected to the diverter port (303); the first swirl blade (302) is arranged in the first diverter chamber (311); one end of the second diverter chamber (312) is connected to the second flow channel (205), and the other end of the second diverter chamber (312) is connected to the diverter port (303).

6. The heat exchanger according to claim 5, characterized in that The diversion port (303) is provided with a liquid separation component (5), and the liquid separation component (5) comprises a first branch pipe (501), a second branch pipe (502) and a diverter (503); one end of the first branch pipe (501) and the second branch pipe (502) are both connected to the first cover body (301), and the first branch pipe (501) is communicated with the first diversion cavity (311), and the second branch pipe (502) is communicated with the second diversion cavity (312); the other ends of the first branch pipe (501) and the second branch pipe (502) are both connected to the diverter (503).

7. The heat exchanger according to claim 3, characterized in that: The refrigerant flow rate in the diverter pipe (204) is greater than the refrigerant flow rate in the tube body (203), and the cross-sectional area of ​​the second flow channel (205) is smaller than the cross-sectional area of ​​the first flow channel (201).

8. The heat exchanger according to claim 3, characterized in that: The second swirl member (4) comprises a second cover body (401) and a second swirl blade (402); one end of the second cover body (401) is connected to the second end (22); the other end of the second cover body (401) is sealed; the second swirl blade (402) is arranged in the second cover body (401); and the first flow channel (201) and the second flow channel (205) are both connected to the second cover body (401).

9. The heat exchanger according to claim 8, characterized in that A partition plate (403) is provided in the second cover body (401), and the partition plate (403) divides the inner cavity of the second cover body (401) into a first chamber (431) and a second chamber (432), the first chamber (431) is connected to the first flow channel (201), and the second swirl blade (402) is arranged in the first chamber (431); the second chamber (432) is connected to the second flow channel (205), and a connecting hole (433) for connecting the first chamber (431) and the second chamber (432) is provided on the partition plate (403).

10. An air conditioner, comprising a heat exchanger, characterized in that: The heat exchanger is the heat exchanger according to any one of claims 1 to 9.

Images