CN211317039U - Fin of heat exchanger, heat exchanger and air conditioner - Google Patents
Fin of heat exchanger, heat exchanger and air conditioner Download PDFInfo
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- CN211317039U CN211317039U CN201921879738.4U CN201921879738U CN211317039U CN 211317039 U CN211317039 U CN 211317039U CN 201921879738 U CN201921879738 U CN 201921879738U CN 211317039 U CN211317039 U CN 211317039U
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Abstract
The utility model provides a fin, heat exchanger and air conditioner of heat exchanger, wherein, the fin includes the fin, and on the fin was located to the fin, and was located in the heat exchanger around the outside of pipe wall, the distance between the point on the inner wall of fin to the axle center of pipe wall was distance R, and distance R dwindles from the leading edge to the trailing edge direction of fin gradually.
Description
Technical Field
The utility model relates to an air conditioner technical field particularly, relates to a fin, heat exchanger and air conditioner of heat exchanger.
Background
In recent years, with the development of air conditioning technology and the improvement of energy efficiency standards of air conditioners at home and abroad, the requirement on the heat exchange efficiency of a heat exchanger is continuously improved in order to meet the requirement on the energy efficiency of the air conditioners.
The heat exchange thermal resistance of the existing heat exchanger is mainly air side heat exchange thermal resistance, so the heat exchanger strengthening technical method is mainly to carry out optimization design on air side fins, thereby improving the performance of the heat exchanger and further improving the performance of an air conditioner. Although the heat exchange capacity of the existing fin heat exchanger can be improved in a mode of enhancing air disturbance, the heat exchange capacity of the heat exchanger is improved to a limited extent because the flow resistance of the air side is increased in the mode.
SUMMERY OF THE UTILITY MODEL
In order to solve at least one problem, the utility model provides a fin of heat exchanger, the fin includes the fin, the fin is located on the fin, and be located around the outside of pipe wall in the heat exchanger, point on the inner wall of fin arrives distance between the axle center of pipe wall is distance R, distance R follows the leading edge to the trailing edge direction of fin dwindles gradually.
Adopt above-mentioned technical scheme, the utility model discloses on the basis of current heat exchanger, through setting up the fin, specifically locate the fin on the fin, and be located around the outside of pipe wall, simultaneously point on the inner wall of fin arrives distance between the axle center of pipe wall is distance R, distance R follows the leading edge to the trailing edge direction of fin dwindles gradually. The utility model discloses the longitudinal vortex principle of make full use of and efflux principle, after the air current flows through the fin, can be at the trailing edge of fin, also be exactly the afterbody of fin forms a series of longitudinal vortexes, simultaneously, the point on the inner wall of fin arrives distance between the axle center of pipe wall is distance R, distance R follows the leading edge of fin is dwindled to the trailing edge direction gradually, makes the air current follow the pipe wall rear that the fin flow to the pipe wall with higher speed to form the efflux, in order to slow down the flow separation of air current and pipe wall, reduces the weak heat transfer area at pipe wall rear, makes near pipe wall heat transfer effect obviously promote.
Optionally, the height h of the vane gradually increases from the leading edge to the trailing edge of the vane. This configuration facilitates the formation of longitudinal vortices at the trailing edge of the airfoil.
Optionally, the range of an included angle γ between the outer side surface of the fin and the surface where the fin is located is as follows: gamma is more than or equal to 45 degrees and less than or equal to 90 degrees. The structure can ensure the contact area of the airflow and the fins, and is convenient for slowing down the flow separation of the airflow and the pipe wall after the jet flow is formed.
Optionally, the distance R is equal to the minimum inner surface radius R of the pipe wall0Satisfies the following relationship: r ═ 1.02-1.3) R0. The structure is such that the minimum inner surface radius R passing through the pipe wall0And the distance R is limited, so that the distance between the fin and the pipe wall can be effectively ensured, and the optimal effect is ensured.
Optionally, the number of the fins is more than one group. With the structure, the number of the fins can be selected according to specific requirements, and the number of the fins is preferably two.
Optionally, when the number of the fins is two, the two fins are symmetrically distributed on two sides of the pipe wall, and the symmetric plane passes through the axis of the pipe wall. According to the structure, after the airflow passes through the two groups of fins, the speed and other states are similar, so that the flowing conditions of the two sides of the pipe wall are consistent, the heat dissipation is uniform, and the phenomenon of uneven heat dissipation is avoided.
Optionally, a projection of the inner wall of the fin on the surface of the fin and a minimum included angle θ formed between the projection and the incoming flow direction1The value range is as follows: 0 degree<θ1<30 deg. The structure is such that the angle of the line passing through the line to the minimum angle theta1The limiting device can ensure that a certain distance is reserved between one end, far away from the incoming flow direction, of the fin and the pipe wall, airflow can flow through the fin conveniently, and meanwhile, the distance can ensure that the airflow flows through the jet flow formed after flowing through the fin, so that the flowing separation of the airflow and the pipe wall can be slowed down.
Optionally, a projection of the inner wall of the fin on the surface of the fin and a maximum included angle θ formed between the projection and the incoming flow direction2The value range is as follows: 10 degree<θ2<45 degrees. The structure is characterized in thatLarge included angle theta2The limiting device can ensure that a certain distance is reserved between the fins and the pipe wall, so that airflow can flow through the fins conveniently, and meanwhile, the distance can ensure that the airflow can form jet flow after flowing through the fins.
Optionally, a connecting line between a leading edge point of the outer edge of the pipe wall closest to the inflow port and a point of the central axis of the pipe wall is OA, a connecting line between a point of the wing on the inner wall of the leading edge and a point of the central axis of the pipe wall is OB in a projection of a plane where the wing is located, and an included angle formed by OA and OB is α1Said α1The value range is as follows: 45 degree<α1<90 deg. this arrangement, by pair α1The limiting device can ensure that a certain distance is reserved between the fins and the pipe wall, so that airflow can flow through the fins conveniently, and meanwhile, the distance can ensure that the airflow flows through the fins to form jet flow, so that the flowing separation of the airflow and the pipe wall can be slowed down.
Optionally, a connecting line between a leading edge point of the outer edge of the pipe wall closest to the inflow port and a point of the central axis of the pipe wall is OA, a connecting line between a point of the wing on the inner wall of the trailing edge and a point of the central axis of the pipe wall is OC in a projection of a plane where the wing is located, and an included angle formed by the OA and the OC is α2Said α2The value range is as follows: 100 degree<α2<150 deg. this construction, by pair α2The limiting device can ensure that a certain distance is reserved between the fins and the pipe wall, so that airflow can flow through the fins conveniently, and meanwhile, the distance can ensure that the airflow can form jet flow after flowing through the fins.
Optionally, the tab comprises more than one tab. The structure can be convenient for adjusting the structure of the fin and the like, and is convenient for processing the fin.
Optionally, when the number of the small fins is more than two, the small fins include a first small fin and a second small fin, the number of the first small fin is one, the number of the second small fin is more than one, and the first small fin and the second small fin are sequentially arranged from the leading edge to the trailing edge of the fin. This kind of structure, the air current is when the fin of flowing through, at first with first winglet piece contact, then with second winglet piece contact again, consequently the area of contact of air current and fin can crescent, is favorable to reducing the flow loss of air current and fin initial contact position, makes the air current change direction under the fin effect more naturally, forms the efflux, further slows down the flow separation of air current and pipe wall, reduces the weak heat transfer area at pipe wall rear, promotes near the heat transfer effect of pipe wall.
Optionally, the first tab is triangular, and the second tab is quadrilateral; or both the first winglet and the second winglet are quadrilateral. According to the structure, the contact area of the airflow and the fins can be gradually increased, the flow separation of the airflow and the pipe wall can be slowed down, the weak heat exchange area behind the pipe wall is reduced, and the heat exchange effect nearby the pipe wall is improved.
Optionally, the fin includes a hollow slot, and the hollow slot is disposed outside the fin. The structure is convenient for the joint processing of the fin and the hollow slot and the one-time forming. In addition, the fretwork is slotted and can also be increased the speed and the disturbance degree that the air current flows, can effectual intensive heat transfer effect. Moreover, the fretwork is slotted and can be convenient for frost, ash, water and the like to timely flow out through the fretwork is slotted, and the reduction of the heat exchange efficiency of the heat exchanger is avoided.
Optionally, the fin with the fretwork is slotted and is disposable stamping forming. This kind of mode, the processing of fin and fretwork crack of being convenient for.
Optionally, the number of the fins is multiple, the multiple fins are stacked, and the tube wall is arranged in the stacked fins in a penetrating manner. The structure is convenient for manufacturing heat exchangers with different specifications according to specific conditions. The refrigerant can flow in the pipe wall, and can flow in other pipes such as copper pipes and the like arranged in the pipe wall.
Optionally, the distance H between two adjacent fins is greater than the maximum height H of the finmax. This kind of structure is convenient for protect the structure of fin, avoids the fin when the superpose equipment, causes the damage to the fin.
The utility model also provides a heat exchanger, the heat exchanger includes fin and pipe wall, the heat exchanger includes above-mentioned arbitrary any the fin.
Optionally, the number of the pipe walls is multiple, the pipe walls are distributed in multiple rows, the pipe walls in the same row are distributed at intervals, and the pipe walls in adjacent rows are distributed in a staggered manner. By the mode, the contact area between the airflow and the pipe wall can be increased, the air disturbance is enhanced, and the heat exchange efficiency is effectively improved.
The utility model also provides an air conditioner, the air conditioner include above-mentioned arbitrary any the heat exchanger.
Drawings
Fig. 1 is a schematic view of a partial three-dimensional structure of a fin of a heat exchanger according to the present invention;
fig. 2 is a partial top view of a fin of a heat exchanger according to the present invention;
fig. 3 is a partial side view of a fin of a heat exchanger according to the present invention;
fig. 4 is a partial side view of a fin of a heat exchanger of the present invention;
fig. 5 is a partial side view of a fin of a heat exchanger according to the present invention;
fig. 6 is a schematic view of a partial three-dimensional structure of a fin of a heat exchanger according to the present invention (with a hollow slit);
fig. 7 is a partial top view (with hollow slits) of a fin of a heat exchanger according to the present invention;
fig. 8 is a schematic perspective view of a heat exchanger according to the present invention;
fig. 9 is an experimental diagram of the flow field difference of the heat exchanger of the present invention.
Description of reference numerals:
10-a fin; 110-a fin; 111-small fins; 1111-a first tab; 1112-a second tab; 120-hollowing and slotting; 20-tube wall.
Detailed Description
It should be noted that, in the present invention, the embodiments and features of the embodiments may be combined with each other without conflict.
In order to make the aforementioned objects, features and advantages of the present invention more comprehensible, embodiments accompanied with figures are described in detail below.
Example 1
As shown in fig. 1, the present invention provides a heat exchanger fin, the fin 10 includes a fin 110, the fin 110 is disposed on the fin 10 and is located around the outer side of the tube wall 20 in the heat exchanger; the distance between a point on the inner wall of the airfoil 110 and the axis of the duct wall 20 is a distance R, which gradually decreases from the leading edge to the trailing edge of the airfoil 110.
The utility model discloses on current heat exchanger's basis, through setting up fin 110, specifically locate fin 110 on fin 10, and be located around the outside of pipe wall 20, the distance between the point on fin 110's the inner wall to the axle center of pipe wall 20 is distance R simultaneously, and distance R reduces from fin 110's leading edge to trailing edge direction gradually. The utility model discloses the vertical vortex principle of make full use of and efflux principle, after the air current flows through fin 110, can be at fin 110's trailing edge, also be that fin 110's afterbody forms a series of vertical vortexes, and simultaneously, the distance between the axle center of point to pipe wall 20 on fin 110's the inner wall is distance R, distance R reduces from fin 110's leading edge to trailing edge direction gradually, make the air current follow fin 110 with higher speed the pipe wall rear that flows to pipe wall 20, form the efflux, in order to slow down the separation of flow with pipe wall 20, reduce the weak heat transfer area at pipe wall 20 rear, make near pipe wall 20 heat transfer effect obviously promote.
Wherein the distance R from a point on the inner wall of the leading edge of the airfoil 110 to the axis of the tube wall 20 is the maximum distance RmaxThe distance R from a point on the inner wall of the trailing edge of the airfoil 110 to the axis of the tube wall 20 is the minimum distance Rmin。
The inner wall of the fin 110 is the side wall of the fin 100 on the side near the tube wall 20.
In some embodiments, the height h of the airfoil 110 increases gradually from the leading edge to the trailing edge of the airfoil 110. This configuration facilitates the formation of longitudinal vortices at the trailing edge of the airfoil 110.
In some embodiments, the included angle γ between the outer side surface of the fin 110 and the surface of the fin 10 is in the range: gamma is more than or equal to 45 degrees and less than or equal to 90 degrees. With the structure, the contact area between the airflow and the fins 110 can be ensured, and the separation of the airflow and the flow of the pipe wall 20 can be slowed down after the jet flow is formed.
As shown in FIG. 2, in some embodiments, distance R is related to the minimum inner surface radius R of tube wall 200Satisfies the following relationship: r ═ 1.02-1.3) R0. This configuration, through the minimum inner surface radius R of the tube wall 200The distance R is limited, so that the distance between the fins 110 and the pipe wall 20 can be effectively ensured, and the optimal effect can be ensured. For example, when the value of R0 is 11mm, the value of R ranges from 11.22mm to 14.3 mm.
In some embodiments, the number of fins 110 is more than one group. With this configuration, the number of fins 110 can be selected according to specific needs, and the number of fins 110 is preferably two.
In the present embodiment, when the number of the fins 110 is two, the two fins 110 are symmetrically distributed on two sides of the tube wall 20, and the symmetric plane is through the axis of the tube wall 20. With the structure, after the airflow passes through the two groups of fins 110, the speed and other states are similar, so that the flowing conditions on the two sides of the pipe wall are consistent, the heat dissipation is uniform, and the phenomenon of uneven heat dissipation is avoided.
As shown in FIG. 2, in some embodiments, the projection of the inner wall of the fin 110 on the surface of the fin 10 forms a minimum angle θ with the incoming flow direction1The value range is as follows: 0 degree<θ1<30 deg. Wherein the minimum angle theta1When the number of the small fins 111 is two or more, that is, the projection of the inner wall of the leading edge of the fin 110 on the surface of the fin 10 forms an included angle with the incoming flow direction, that is, the projection of the inner wall of the first winglet 1111 on the surface of the fin 10 forms an included angle with the incoming flow direction. The smaller the angle between the projection of the inner wall of the fin 110 on the surface of the fin 10 and the incoming flow direction is, the farther the end of the fin 110 away from the incoming flow direction is from the pipe wall 201The limitation of (2) can ensure that a certain distance is formed between one end of the fin 110 far away from the incoming flow direction and the pipe wall 20, so that the airflow can conveniently flow through the fin 110, and the distance can ensure that the jet flow formed after the airflow flows through the fin 110 can slow down the flow of the airflow and the pipe wall 20And (5) separating.
In some embodiments, the projection of the inner wall of the fin 110 on the surface of the fin 10 forms a maximum included angle θ with the incoming flow direction2The value range is as follows: 10 degree<θ2<45 degrees. Wherein the maximum included angle theta2When the number of the small vanes 111 is two or more, that is, the second winglet 1112 farthest from the first winglet 1111, the projection of the inner wall of the second winglet 1112 on the plane of the fin 10 forms an angle with the incoming flow direction. The larger the angle between the projection of the inner wall of the fin 110 on the surface of the fin 10 and the incoming flow direction is, the closer the end of the fin 110 away from the incoming flow direction is to the pipe wall 202The distance between the fins 110 and the tube wall 20 is ensured to facilitate the airflow passing through the fins 110, and the distance ensures that the airflow forms a jet after passing through the fins 110.
In some embodiments, the line connecting the leading edge of the outer edge of the tube wall 20 closest to the inflow opening to the central axis of the tube wall 20 is OA, the line connecting the point of the inner wall of the leading edge of the airfoil 110 to the central axis of the tube wall 20 is OB in the projection of the plane of the fin 10, and the included angle formed by OA and OB is α1，α1The value range is as follows: 45 degree<α1<90 DEG therein, α1I.e., ∠ AOB. this configuration, via pair α1The distance between the fins 110 and the pipe wall 20 can be ensured, so that the airflow can conveniently flow through the fins 110, and the distance can ensure that the jet flow formed after the airflow flows through the fins 110 can slow down the flow separation of the airflow and the pipe wall 20.
In some embodiments, the line connecting the leading edge of the outer edge of the tube wall 20 closest to the inflow opening to the central axis of the tube wall 20 is OA, the line connecting the point of the inner wall of the trailing edge of the airfoil 110 to the central axis of the tube wall 20 is OC in the plane of the fin 10, and the included angle formed by OA and OC is α2，α2The value range is as follows: 100 degree<α2<150 deg. of which α2I.e., ∠ AOC. this configuration, via pair α2The distance between the fins 110 and the tube wall 20 is ensured to facilitate the airflow passing through the fins 110, and the distance ensures that the airflow forms a jet after passing through the fins 110.
As shown in fig. 3-5, in some embodiments, the tab 110 includes more than one tab 111. This structure can facilitate adjustment of the structure and the like of the fin 110, and facilitate processing of the fin 110.
In the present embodiment, when the number of the winglet 111 is two or more, the winglet 111 includes a first winglet 1111 and a second winglet 1112, the number of the first winglet 1111 is one, the number of the second winglet 1112 is one or more, and the first winglet 1111 and the second winglet 1112 are arranged in order from the leading edge to the trailing edge of the winglet 110; the first winglet 1111 is triangular in shape and the second winglet 1112 is quadrilateral in shape; or both the first winglet 1111 and the second winglet 1112 may be quadrilateral. The quadrilateral is preferably a trapezoid, and two parallel sides of the trapezoid are perpendicular to the plane of the fin 10. With the structure, when the airflow flows through the wing 110, the airflow firstly contacts with the first winglet 1111 and then contacts with the second winglet 1112, so that the contact area of the airflow and the wing 110 is gradually increased, which is beneficial to reducing the flow loss of the initial contact position of the airflow and the wing, the airflow changes direction more naturally under the action of the wing to form jet flow, further slowing down the flow separation of the airflow and the pipe wall 20, reducing the weak heat exchange area behind the pipe wall 20, and improving the heat exchange effect near the pipe wall 20.
In some embodiments, the number of the fins 10 is plural, a plurality of the fins 10 are stacked, and the tube wall 20 is inserted into the stacked fins 10. The structure is convenient for manufacturing heat exchangers with different specifications according to specific conditions. The refrigerant may flow in the tube wall 20, or may flow in other tubes, such as a copper tube, built in the tube wall 20.
In the present embodiment, the distance H between two adjacent fins 10 is larger than the maximum height H of the fin 110max. The structure is convenient for protecting the structure of the fin 110 and preventing the fins 10 from being stackedDamage to the fins 110 occurs during assembly.
As shown in fig. 6-7, in some embodiments, the fin 10 includes an open slot 120, the open slot 120 being disposed on the outside of the airfoil 110. Preferably, the shape of the slits 120 is the same as the shape of the fins 110. According to the structure, the shape of the hollowed-out seam 120 is the same as that of the fin 110, so that the fin 110 and the hollowed-out seam can be processed together conveniently and can be formed at one time. In addition, the fretwork cracks 120 and can also increase the speed and the disturbance degree that the air current flows, can effectual intensive heat transfer effect. Moreover, the fretwork is slotted 120 and can be convenient for frost, ash, water etc. timely to be slotted 120 outflow through the fretwork, avoids heat exchanger heat exchange efficiency's reduction.
In the present embodiment, the fins 110 and the hollow slits 120 are formed by one-time press molding. In this manner, the processing of the fins 110 and the slots 120 is facilitated.
Example 2
As shown in fig. 8, the present invention further provides a heat exchanger, which comprises fins 10 and a tube wall 20, wherein the heat exchanger comprises any one of the fins 110.
The copper pipe penetrates through the pipe wall 20, the refrigerant inside the copper pipe transfers the temperature to the copper pipe, the copper pipe transfers the temperature to the fins 10 through the contact surface of the copper pipe and the pipe wall 20, and air flows through the fins 10 to realize the heat convection of the heat exchanger.
In some embodiments, there are a plurality of tube walls 20, a plurality of tube walls 20 are arranged in a plurality of rows, the same row of tube walls 20 are arranged at intervals, and the adjacent rows of tube walls 20 are arranged in a staggered manner. By adopting the mode, the contact area between the airflow and the pipe wall 20 can be increased, the air disturbance is enhanced, and the heat exchange efficiency is effectively improved.
It is further right the utility model discloses a heat exchanger effect explains, the utility model discloses a following mode is right the utility model discloses a heat exchanger effect explains.
Adopt CFD simulation method, under the simulation same condition, ordinary plain film fin 10's heat exchanger with the utility model discloses a flow field difference of heat exchanger. The inlet and outlet static pressure difference (outlet static pressure value minus inlet static pressure value) -20Pa is used for replacing the action of a fan on a heat exchanger under the high-speed air working condition of an air conditioner indoor unit, the ambient temperature is set to be 27 ℃, the inner surface of the pipe wall 20 is set to be constant temperature of 12 ℃ so as to replace the action of a refrigerant in a copper pipe of the heat exchanger, and fluent software is used for calculation to obtain the result shown in figure 7.
Fig. 9 is a velocity cloud chart of the cross section of the heat exchanger (left side view) of the conventional flat fin 10 and the heat exchanger (right side view) of the present invention at the same position. It can be seen that the utility model discloses an effect of fin 110 makes near the airflow velocity of flow of pipe wall 20 obviously be greater than the plain film, has slowed down the flow separation around the pipe wall 20, makes the weak heat transfer district in pipe wall 20 rear (black region) obviously reduce.
Example 3
The utility model also provides an air conditioner, the air conditioner include above-mentioned arbitrary any the heat exchanger.
The leading edge of the airfoil 110 of the present invention refers to: near the location of the inflow of the gas stream;
the trailing edge of the airfoil 110 refers to: near the point where the air stream flows out;
the incoming flow direction is as follows: the direction of airflow.
Although the present invention is disclosed above, the present invention is not limited thereto. Various changes and modifications may be effected therein by one of ordinary skill in the pertinent art without departing from the scope or spirit of the present invention, and the scope of the present invention is defined by the appended claims.
Claims (19)
1. A fin of a heat exchanger, characterized in that: the fin (10) comprises a fin (110), and the fin (110) is arranged on the fin (10) and is positioned around the outer side of the tube wall (20) in the heat exchanger; the distance between a point on the inner wall of the wing (110) and the axis of the pipe wall (20) is a distance R, and the distance R is gradually reduced from the front edge to the rear edge of the wing (110).
2. The fin of claim 1, wherein: the height h of the airfoil (110) increases gradually from the leading edge to the trailing edge of the airfoil (110).
3. The fin of claim 1, wherein: the range of an included angle gamma between the outer side surface of the fin (110) and the surface of the fin (10) is as follows: gamma is more than or equal to 45 degrees and less than or equal to 90 degrees.
4. The fin of claim 1, wherein: the distance R is related to the minimum inner surface radius R of the pipe wall (20)0Satisfies the following relationship: r ═ 1.02-1.3) R0。
5. The fin of claim 1, wherein: the number of the fins (110) is more than one group.
6. The fin of claim 5, wherein: when the number of the fins (110) is two, the two groups of fins (110) are symmetrically distributed on two sides of the pipe wall (20).
7. The fin of claim 1, wherein: the projection of the inner wall of the fin (110) on the surface of the fin (10) and the minimum included angle theta formed by the incoming flow direction1The value range is as follows: 0 degree<θ1<30°。
8. The fin of claim 1, wherein: the projection of the inner wall of the fin (110) on the surface of the fin (10) and the maximum included angle theta formed by the incoming flow direction2The value range is as follows: 10 degree<θ2<45°。
9. The fin according to claim 1, wherein a connecting line between a leading edge point of the outer edge of the tube wall (20) closest to the inflow port and a point of the central axis of the tube wall (20) is OA, a connecting line between a point of the inner wall of the leading edge of the fin (110) and a point of the central axis of the tube wall (20) is OB in a projection on a plane where the fin (10) is located, and an included angle formed by OA and OB is α1Said α1The value range is as follows: 45 degree<α1<90°。
10. The fin according to claim 1, wherein a connecting line between a leading edge point of the outer edge of the tube wall (20) closest to the inflow port and a point of the central axis of the tube wall (20) is OA, a connecting line between a point of the inner wall of the trailing edge of the fin (110) and a point of the central axis of the tube wall (20) is OC in a projection on a plane where the fin (10) is located, and an included angle formed by OA and OC is α2Said α2The value range is as follows: 100 degree<α2<150°。
11. The fin of claim 1, wherein: the fin (110) includes one or more small fins (111).
12. The fin of claim 11, wherein: when the number of the small vanes (111) is two or more, the small vanes (111) include a first small vane (1111) and a second small vane (1112), the number of the first small vane (1111) is one, the number of the second small vane (1112) is one or more, and the first small vane (1111) and the second small vane (1112) are sequentially arranged from the leading edge to the trailing edge direction of the vane (110).
13. The fin of claim 12, wherein: the first small fin (1111) is triangular in shape, and the second small fin (1112) is quadrangular in shape; or the first winglet (1111) and the second winglet (1112) are both quadrilateral.
14. The fin of claim 1, wherein: the distance H between two adjacent fins (10) is larger than the maximum height H of the fin (110)max。
15. The fin of claim 1, wherein: the fin (10) comprises a hollow seam (120), and the hollow seam (120) is arranged on the outer side of the fin (110).
16. The fin of claim 15, wherein: the fin (110) and the hollowed-out slot (120) are formed in a one-time stamping mode.
17. A heat exchanger comprising a tube wall (20), characterized in that: the heat exchanger further comprising a fin as recited in any one of claims 1 to 16.
18. The heat exchanger of claim 17, wherein: the number of the pipe walls (20) is multiple, the pipe walls (20) are distributed in multiple rows, the pipe walls (20) in the same row are distributed at intervals, and the pipe walls (20) in adjacent rows are distributed in a staggered mode.
19. An air conditioner, characterized in that: the air conditioner comprising the heat exchanger of any one of claims 17-18.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921879738.4U CN211317039U (en) | 2019-11-04 | 2019-11-04 | Fin of heat exchanger, heat exchanger and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921879738.4U CN211317039U (en) | 2019-11-04 | 2019-11-04 | Fin of heat exchanger, heat exchanger and air conditioner |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN211317039U true CN211317039U (en) | 2020-08-21 |
Family
ID=72080201
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201921879738.4U Active CN211317039U (en) | 2019-11-04 | 2019-11-04 | Fin of heat exchanger, heat exchanger and air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN211317039U (en) |
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2019
- 2019-11-04 CN CN201921879738.4U patent/CN211317039U/en active Active
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