CN217716083U - Pipe fin monomer, heat exchanger and air conditioner - Google Patents

Abstract

The utility model discloses a pipe wing monomer, heat exchanger and air conditioner. The tube fin single body comprises a substrate, wherein the substrate is a corrugated sheet, the substrate comprises fin parts and flow channel parts which are alternately arranged, and a refrigerant channel is arranged in the flow channel part; the refrigerant channel is bent and extended along a first direction, and an included angle alpha between the corrugation direction of the corrugated sheet and the first direction is as follows: alpha is more than or equal to 0 degree and less than 90 degrees. The substrate of the tube fin monomer is a corrugated sheet, so that the tube fin monomer has a self-supporting function, the sheet distance between the tube fin monomers can be limited, the structure of the tube fin monomer is simplified, the requirements of a 3D metal printing manufacturing process are met, and the tube fin monomer is prevented from being broken due to the fact that no supporting structure exists between the tube fin monomers.

Description

Pipe fin monomer, heat exchanger and air conditioner

Technical Field

The utility model relates to a but not limited to the air conditioning equipment field, in particular to but not limited to a pipe wing monomer, a heat exchanger and an air conditioner.

Background

Copper pipes and fins of the existing finned tube heat exchanger for mass production are assembled in an expansion joint mode; the mass-produced micro-channel heat exchanger is also produced by adopting flat pipes and fins separately, and is assembled in an integral welding mode after being assembled.

The copper tube and the fins of the prior finned tube heat exchanger have thermal contact resistance in an expansion assembly mode, so that the heat transfer efficiency is low; although the micro-channel heat exchanger adopts a welding form to reduce the contact thermal resistance, the flat tube and the fin are separately produced and are assembled and welded, so that the process is complex, the production efficiency is low and the cost is high.

SUMMERY OF THE UTILITY MODEL

The embodiment of the utility model provides a main objective provides a pipe wing monomer has the self-supporting function, and processing technology is simple, and has avoided the thermal resistance between fin portion and the runner portion, guarantees the heat transfer ability of heat exchanger.

In order to achieve the above purpose, the technical scheme of the utility model is as follows:

the embodiment of the utility model provides a pipe wing monomer, include: the substrate is a corrugated sheet and comprises fin parts and flow channel parts which are alternately arranged, and a refrigerant channel is arranged in each flow channel part;

the refrigerant channel is bent and extended along a first direction, and an included angle alpha between the corrugation direction of the corrugated sheet and the first direction is as follows: alpha is more than or equal to 0 degree and less than 90 degrees.

In some exemplary embodiments, 30 ≦ α ≦ 60.

In some exemplary embodiments, along the corrugation direction of the corrugated sheet, the relationship between the length L1 of the corrugated sheet and the single wavelength L2 is: 2 XL₂≤L₁≤5×L₂。

In some exemplary embodiments, 8mm ≦ L₂≤12mm。

In some exemplary embodiments, the wave height H of the corrugated sheet is: h is more than or equal to 0.8mm and less than or equal to 1.6mm.

In some exemplary embodiments, the substrate is an integrally formed structure formed by a 3D metal printing process.

In some exemplary embodiments, the inner diameter of the refrigerant channel is not greater than 0.4mm, and the thickness of the fin part is not greater than 0.4mm.

The embodiment of the utility model provides a still provide a heat exchanger, include: the fin type heat exchanger comprises a first collecting pipe, a second collecting pipe and a plurality of fin single bodies in any embodiment, wherein the fin type heat exchanger is characterized in that the fin type heat exchanger comprises a plurality of fin single bodies, the fin type heat exchanger comprises a plurality of first collecting pipes and a plurality of second collecting pipes, the fin type heat exchanger comprises a plurality of fin single bodies, the fin type heat exchanger comprises a plurality of first fin bodies and a plurality of fin single bodies, the fin type heat exchanger comprises a plurality of fin single bodies, the fin type fin single bodies are arranged in parallel, wave bands protruding towards each other of the adjacent fin type single bodies are abutted against each other, one end of each fin type single body is connected with the first collecting pipe, one end of each fin type single body is connected with the second collecting pipe, and the other ends of the fin type fin single bodies are connected with the first collecting pipes and the second collecting pipes.

In some exemplary embodiments, two adjacent tube fin units are symmetrically arranged about a symmetry line, and the symmetry line is parallel to the first direction along which the refrigerant channel extends.

In some exemplary embodiments, the first header, the plurality of tube fin units and the second header are a one-piece structure formed by a 3D metal printing process, and the fin portions or the flow channel portions of the tube fin units are disposed in contact with the fin portions or the flow channel portions of the adjacent tube fin units; or alternatively

The first collecting pipe, the plurality of tube fin monomers and the second collecting pipe are of a split type assembly structure, one end of each tube fin monomer is connected with the first collecting pipe in an inserting mode, the other end of each tube fin monomer is connected with the second collecting pipe in an inserting mode, and the adjacent two tube fin parts of the tube fin monomers are in contact.

In some exemplary embodiments, an air duct is formed between two adjacent tube fin units, and the air duct is gradually inclined downwards along the flowing direction of the wind.

In some exemplary embodiments, the sheet distance S between two adjacent tube fin units is: s is more than or equal to 1.2mm and less than or equal to 1.6mm.

In some exemplary embodiments, along the first direction, a distance between two adjacent abutment points of two adjacent fin units is not greater than 7cm;

in the first direction, among a plurality of abutting points of two adjacent tube fin monomers, the distance between the abutting point close to the first collecting pipe and the first collecting pipe is not more than 7cm, and the distance between the abutting point close to the second collecting pipe and the second collecting pipe is not more than 7cm.

The embodiment of the utility model provides a still provide an air conditioner, including above-mentioned arbitrary embodiment the heat exchanger.

The utility model discloses the tube fin monomer of embodiment, its substrate are the ripple piece for when a plurality of tube fin monomers form the heat exchanger, the convex wave band of orientation each other of two adjacent tube fin monomers can butt each other to support the tube fin monomer, prescribe a limit to the piece distance between the tube fin monomer, make this tube fin monomer be the self-supporting tube fin monomer that has the self-supporting function, avoid setting up bearing structure or distance module on the substrate and prescribe a limit to the piece distance, simplified the free structure of tube fin, and strengthened the free structural strength of tube fin; meanwhile, the refrigerant channel of the substrate is bent and extended along a first direction, and an included angle alpha between the corrugation direction of the corrugated sheet and the first direction is as follows: alpha is more than or equal to 0 degree and less than 90 degrees, so that the tube fin single bodies also meet the requirements of a 3D metal printing manufacturing process and the tube fin single bodies are prevented from being broken due to the fact that no supporting structure exists among the tube fin single bodies. In addition, the arrangement of the corrugated structure improves the turbulence degree of air passing through the fin monomers, so that the heat exchange capacity of the heat exchanger is enhanced.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the embodiments or the prior art descriptions will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the structures shown in the drawings without creative efforts.

Fig. 1 is a schematic structural diagram of a heat exchanger according to an embodiment of the present invention;

FIG. 2 is a schematic diagram of a plurality of fin elements of the heat exchanger of FIG. 1;

FIG. 3 is an exploded view of a plurality of the fin units shown in FIG. 2;

FIG. 4 is a schematic structural view of a fin unit of the heat exchanger shown in FIG. 1;

FIG. 5 isbase:Sub>A schematic sectional view taken along line A-A of FIG. 4;

fig. 6 is a schematic structural diagram of a usage state of a heat exchanger according to an embodiment of the present invention.

The reference signs are:

100-heat exchanger, 1-single tube fin, 11-substrate, 111-fin part, 112-runner part, 113-refrigerant channel, 12-air channel, 13-ascending wave band, 14-descending wave band, 2-first collecting pipe, 21-first inlet and outlet, 3-second collecting pipe, 31-second inlet and outlet, and 4-fan.

The objects, features and advantages of the present invention will be further described with reference to the accompanying drawings.

Detailed Description

The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts belong to the protection scope of the present invention.

As shown in fig. 1, the embodiment of the present invention provides a tube fin unit 1, and the tube fin unit 1 can be applied to a heat exchanger 100.

As shown in fig. 2 to 4, the fin unit 1 is provided to include: the substrate 11, the substrate 11 is a corrugated sheet, and the substrate 11 includes a fin portion 111 and a flow channel portion 112 alternately arranged, and a coolant channel 113 is provided in the flow channel portion 112.

The cooling medium channels 113 of the tube fin single bodies 1 are used for the cooling medium to flow through, and the fin portions 111 alternately arranged with the flow channel portions 112 increase the contact area between the tube fin single bodies 1 and the air, so that the heat exchange effect between the cooling medium flowing through the cooling medium channels 113 and the air can be improved.

The substrate 11 is a corrugated sheet, and the substrate 11 may be an integrally formed structure. The corrugated sheet has a rising band 13 and a falling band 14 (shown in fig. 5), the rising band 13 and the falling band 14 being separated by a separation line (shown by a dotted line in fig. 5) between peaks and valleys of the corrugated sheet, the rising band being a band on the side of the peak, and the falling band being a band on the side of the valley.

When a plurality of tube fin single bodies 1 form the heat exchanger 100, the convex wave bands of two adjacent tube fin single bodies are mutually abutted, that is, the rising wave band 13 of the corrugated sheet of one tube fin single body 1 can be abutted with the falling wave band 14 of the corrugated sheet of the other adjacent tube fin single body 1 to limit the sheet pitch between the tube fin single bodies 1, that is, the tube fin single body 1 is a self-supporting tube fin single body with a self-supporting function, and the situation that a supporting structure or a distance module is additionally arranged on the substrate 11 to limit the sheet pitch is avoided, so that the structure of the tube fin single body 1 is simplified, the structural strength of the tube fin single body 1 is enhanced, the requirements of a 3D metal printing manufacturing process are met, and the phenomenon of breakage caused by no supporting structure between the tube fin single bodies 1 is prevented. In addition, the arrangement of the corrugated structure improves the turbulence degree of air passing through the fin monomers 1, so that the heat exchange capacity of the heat exchanger 100 is enhanced.

The substrate 11 has an integrated structure, so that the processing technology of the tube fin unit 1 is simplified, and the thermal resistance between the fin part 111 and the flow channel part 112 is avoided, so as to improve the heat exchange efficiency of the heat exchanger 100.

In some exemplary embodiments, as shown in fig. 4, the cooling medium channel 113 extends in a curved manner along a first direction (as indicated by the double-headed arrow in fig. 4), and since the substrate 11 is a corrugated sheet, the cooling medium channel 113 extending along the first direction is a curved channel as a whole. In the embodiment of the present application, the first direction may be a direction in which a connection line between a plurality of lowest points (or a plurality of highest points) of the same flow path portion 112 is located; alternatively, the first direction may also be understood as a vertical direction in which the end portions of the fin bodies 1 (i.e., the end portions of the flow path portions 112) are arranged in a horizontal plane (or in 3D printing).

An angle α between a corrugation direction (a direction indicated by an arrow D in fig. 4) of the corrugated sheet and a first direction along which the refrigerant channel 113 extends is: alpha is more than or equal to 0 degree and less than 90 degrees. In some embodiments, 30 ≦ α ≦ 60, such as: the included angle α may be 35 °, 40 °, 45 °, 50 °, 55 °, etc. In the embodiment of the application, the corrugation direction is a direction which is perpendicular to the straight line where each wave crest is located and passes through the straight lines of the plurality of wave crests; or the direction of the straight line which is perpendicular to each trough and passes through a plurality of troughs.

The corrugation direction of the corrugated sheet, i.e. the propagation direction of the corrugations, is perpendicular to the crest line or the trough line of the corrugated sheet, and the included angle α between the corrugation direction of the corrugated sheet and the first direction along which the refrigerant channel 113 extends: alpha is more than or equal to 0 degree and less than 90 degrees, namely the corrugation direction of the corrugated sheet can be parallel to the direction of the first direction along which the refrigerant channel 113 extends (alpha =0 degrees), or the corrugation direction of the corrugated sheet can be obliquely arranged relative to the first direction along which the refrigerant channel 113 extends (alpha is more than 0 degrees and less than 90 degrees), namely the corrugation on the corrugated sheet is oblique corrugation, so that the substrate 11 with the self-supporting function can be formed by adopting a 3D metal printing process, the problems that the distance among the tube fin monomers 1 is changed in the printing process, the tube fin monomers 1 are broken due to no support and the like are solved, and further the heat exchange capacity, the production efficiency and the reliability of the heat exchanger 100 are ensured.

In some exemplary embodiments, as shown in FIG. 5, the length L of the corrugated sheet is along the corrugation direction of the corrugated sheet₁The wavelength (distance between two adjacent wave crests or wave troughs) L of the corrugated sheet₂The relationship between them is: 2 xL₂≤L₁≤5×L₂. Such as: l is a radical of an alcohol₁＝3×L₂Or 3.5 XL₂Or 4 XL₂Or 4.5 XL₂。

2×L₂≤L₁≤5×L₂That is, on the substrate 11, there are at least 2 complete waveforms and at most 5 complete waveforms, which are compatible with the requirements of the 3D metal printing manufacturing process of the tube fin unit 1 and the self-supporting function.

Of course, L₁、L₂The relationship between the two is not limited to the above, and can be adjusted according to actual needs, such as L₁≤2×L₂Or L is₁Greater than 5 XL₂。

In some exemplary embodiments, a single wavelength L of the corrugated sheet₂The value range of (A) is as follows: l is more than or equal to 8mm₂12mm or less, such as: wavelength L₂And may be 8.5mm, 9mm, 9.5mm, 10mm, 10.5mm, 11mm, 11.5mm, etc. Based on 2 XL₂≤L₁≤5×L₂Length L of corrugated sheet₁The value ranges of (a) may be: l is not more than 16mm₁≤60mm。

In some exemplary embodiments, the wave height (height difference between the peaks and valleys) H (as shown in fig. 5) of the corrugated sheet is: h is more than or equal to 0.8mm and less than or equal to 1.6mm. Such as: the wave height H may be 0.9mm, 1.0mm, 1.1mm, 1.2mm, 1.3mm, 1.4mm, 1.5mm, etc.

Length L₁Wavelength L of₂The value of the wave height H is related to the through-flow cross-sectional area of the air duct 12 formed between two adjacent tube fin units 1, namely, the wind resistance of the heat exchanger 100, so the length L₁Wavelength L of₂The value of the wave height H is favorable for reducing the wind resistance of the heat exchanger 100.

Of course, the length L₁Wavelength L of₂The value range of the wave height H is not limited to the above, and can be adjusted according to actual needs.

In some exemplary embodiments, substrate 11 is a one-piece structure formed by a 3D metal printing process. The substrate 11 may be made of heat exchange materials such as aluminum alloy and copper alloy.

The flow channel part 112 and the fin part 111 in the tube fin single body 1 are manufactured by adopting an integral forming process, compared with the commonly used finned tube heat exchanger 100 and microchannel heat exchanger 100, the tube expanding and welding process flow is omitted, the production efficiency is improved, the thermal resistance is avoided, and the heat exchange efficiency is improved.

In some exemplary embodiments, the inner diameter (diameter) of the cooling medium channel 113 is not greater than 0.4mm, and the thickness of the fin portion 111 is not greater than 0.4mm.

The thickness of the fin part 111 of the tube fin single body 1 can be set to be 0.4mm or less, the thickness of the fin is too thick, the wind resistance is large, and the cost is high; the fin part 111 is made thinner, so that the wind resistance is reduced, and the fin pitch between the adjacent tube fin units 1 can be reduced to make the heat exchanger 100 more compact while ensuring the same heat exchange amount. The refrigerant channel 113 of the fin unit 1 is a circular hole, and the inner diameter of the refrigerant channel can be set to be 0.4mm or less, so that the refrigerant filling amount in the air conditioning system is reduced, the pipe diameter of the refrigerant channel 113 is small, and the wind resistance of the heat exchanger 100 is also reduced.

It should be understood that the coolant channels 113 on the fin unit 1 may be circular holes or other shapes, such as oval.

In some exemplary embodiments, as shown in fig. 2 to 4, the fin portions 111 are provided in plural numbers (e.g., five), both ends of the substrate 11 in a direction perpendicular to the refrigerant channel 113 may be the fin portions 111, the flow channel portions 112 are provided in at least one number (e.g., four), the fin portions 111 and the flow channel portions 112 are alternately arranged in the direction perpendicular to the refrigerant channel 113, and two adjacent fin portions 111 are separated by one flow channel portion 112, so that the number of the flow channel portions 112 is one less than that of the fin portions 111. If a plurality of flow path portions 112 are provided, the plurality of flow path portions 112 may be arranged at equal intervals. The thickness of the flow path portion 112 is larger than that of the fin portion 111 so that the surface of the flow path portion 112 protrudes from the surface of the fin portion 111.

As shown in fig. 1, the embodiment of the present invention further provides a heat exchanger 100, including: the device comprises a first collecting pipe 2, a second collecting pipe 3 and a plurality of tube fin monomers 1, wherein the tube fin monomers 1 are arranged in parallel, the wave bands, protruding towards each other, of two adjacent tube fin monomers 1 are mutually abutted, one end of each tube fin monomer 1 is connected with the first collecting pipe 2, and the other end of each tube fin monomer 1 is connected with the second collecting pipe 3. The first collecting pipe 2 is provided with a first inlet and a first outlet, and the second collecting pipe 3 is provided with a second inlet and a second outlet.

In the heat exchanger 100, a first collecting pipe 2 and a second collecting pipe 3 are arranged oppositely, a plurality of tube fin single bodies 1 are arranged between the first collecting pipe 2 and the second collecting pipe 3 in parallel, and two ends of the plurality of tube fin single bodies 1 are connected with the first collecting pipe 2 and the second collecting pipe 3 respectively. When the air conditioner including the heat exchanger 100 operates, the refrigerant enters the first header 2 from the first inlet/outlet 21, then is distributed to flow into the refrigerant channel 113 of each fin unit 1, is evaporated or condensed, exchanges heat with external air, then flows into the second header 3, and finally flows out from the second inlet/outlet 31.

In a plurality of tube fin units 1 arranged in parallel, the convex wave bands of two adjacent tube fin units 1 are mutually abutted, that is, the rising wave band (such as a wave peak or a position deviating from the wave peak) of the corrugated sheet of one tube fin unit 1 is contacted with the falling wave band (such as a wave trough or a position deviating from the wave trough) of the corrugated sheet of the adjacent tube fin unit 1, so as to form a support for the tube fin units 1, ensure that the distance between two adjacent tube fin units 1 is unchanged, and improve the heat exchange capability of the heat exchanger 100.

In some exemplary embodiments, two adjacent fin units 1 are symmetrically disposed about a symmetry line, and the symmetry line is parallel to the first direction along which the cooling medium channel 113 extends (see fig. 4).

The plurality of tube fin units 1 arranged in parallel have the same structure, but when the tube fin units are assembled, two adjacent tube fin units 1 are reversely installed. Specifically, as shown in fig. 3, the three fin units 1a, 1b, 1c are identical in structure and are arranged in sequence (only half of the upper and lower fin units 1a and 1c are shown in fig. 3). The state of the tube-fin unit 1b is as shown in fig. 3, and the tube- fin units 1a and 1c adjacent to the tube-fin unit 1b can be obtained by turning 180 degrees in a first direction along which the cooling medium channel 113 extends from an initial state (the same state as that of the tube-fin unit 1 b), so that after the heat exchanger is assembled and formed, the adjacent tube- fin units 1a and 1b are symmetrically arranged about a symmetry line (parallel to the first direction along which the cooling medium channel 113 extends), and the adjacent tube- fin units 1b and 1c are symmetrically arranged about a symmetry line (parallel to the first direction along which the cooling medium channel 113 extends).

As shown in fig. 2 (only a half structure of the upper and lower fin units 1a and 1c is shown), after the heat exchanger is assembled, a contact point (support point) P1 can be formed between the adjacent fin unit 1a and fin unit 1b, and a contact point (support point) P2 can be formed between the adjacent fin unit 1b and fin unit 1c, at this time, the support structures are provided between the adjacent fin units 1 (e.g., between the fin unit 1a and fin unit 1b, and between the fin unit 1b and fin unit 1 c), and the 3D metal printing manufacturing requirements can be met.

In some exemplary embodiments, as shown in fig. 1 and 2, the first header 2, the plurality of fin units 1, and the second header 3 are a unitary structure formed by a 3D metal printing process, and the fin portions 111 or the flow passage portions 112 of the fin units 1 are disposed in contact with the fin portions 111 or the flow passage portions 112 of the adjacent fin units 1.

The two ends of the tube fin single body 1 are respectively connected with the first collecting pipe 2 and the second collecting pipe 3, the first collecting pipe 2, the plurality of tube fin single bodies 1 and the second collecting pipe 3 form an integrated structure in an integral 3D printing mode, the assembling step and the assembling error of the heat exchanger 100 are omitted, and the improvement of the production efficiency and the heat exchange effect is facilitated. Because the heat exchanger 100 is integrally formed by a 3D printing method, the contact points (support points) between two adjacent fin units 1 may be: the contact point between the fin part 111 or the flow channel part 112 of one tube fin unit 1 and the fin part 111 or the flow channel part 112 of another adjacent tube fin unit 1, that is, the contact point on the tube fin unit 1 can be staggered with the flow channel part 112 or does not need to be staggered with the flow channel part 112, and the deformation of the internal refrigerant channel 113 caused by the contact support of the flow channel part 112 can not affect the heat exchange effect of the refrigerant. As shown in fig. 2, the contact point (support point) P1 between the fin unit 1a and the fin unit 1b may be offset from the flow path portions 112 on the fin unit 1a and the fin unit 1b or may not be offset from the flow path portions 112 on the fin unit 1a and the fin unit 1 b; the contact point (support point) P2 between the single tube fin 1b and the single tube fin 1c can be offset from the flow channel portions 112 on the single tube fin 1b and the single tube fin 1c or the flow channel portions 112 on the single tube fin 1b and the single tube fin 1c are not required to be offset, and the refrigerant channels 113 on the single tube fin 1a, the single tube fin 1b and the single tube fin 1c are not deformed.

In other exemplary embodiments, the first header 2, the plurality of tube fin units 1 and the second header 3 are in a split assembly structure, one end of each of the plurality of tube fin units 1 is inserted into the first header 2, the other end of each of the plurality of tube fin units 1 is inserted into the second header 3, and the fin portions 111 of two adjacent tube fin units 1 are in contact.

The first collecting pipe 2, the plurality of tube fin monomers 1 and the second collecting pipe 3 can be of a split type assembly structure, that is, the first collecting pipe 2, the plurality of tube fin monomers 1 and the second collecting pipe 3 can be manufactured and formed respectively (for example, the plurality of tube fin monomers 1 can be formed by a 3D metal printing process respectively), and then one ends of the plurality of tube fin monomers 1 are inserted into the first collecting pipe 2, and the other ends of the plurality of tube fin monomers 1 are inserted into the second collecting pipe 3, so as to assemble the heat exchanger 100. In the assembled heat exchanger 100, the rising wave band of the corrugated sheet of one tube fin unit 1 is abutted against the falling wave band of the corrugated sheet of the adjacent tube fin unit 1 to support the adjacent tube fin unit 1. At this time, the contact points (support points) between two adjacent tube fin units 1 are: the contact points between the fin parts 111 of two adjacent tube fin units 1, namely the contact points on the tube fin units 1 need to stagger the flow channel parts 112, so that the deformation of the internal refrigerant channel 113 caused by the contact support of the flow channel parts 112 is avoided, and the heat exchange effect of the refrigerant is not influenced.

In some exemplary embodiments, the fin unit 1, the first header 2, and the second header 3 may be made of heat exchange material such as aluminum alloy, copper alloy, and the like.

In some exemplary embodiments, as shown in fig. 6, an air duct 12 is formed between two adjacent fin units 1, and the air duct 12 is gradually inclined downward along the flow direction of the wind.

An air duct 12 is formed between every two adjacent tube fin units 1, the corrugated structure on the tube fin units 1 can improve the turbulence degree of air flowing through the air duct 12, and the heat exchange capacity of the heat exchanger 100 can be improved, and for the heat exchanger 100 comprising the flat-plate-type tube fin units 1, the heat exchange efficiency can be improved by about 2%.

The corrugations on the tube fin single bodies 1 are oblique corrugations (namely, 0 degrees < alpha < 90 degrees), and along the flowing direction of wind, the air duct 12 between two adjacent tube fin single bodies 1 is gradually inclined downwards, so that under the action of negative pressure of the fan 4, air flow flows downwards along the air duct 12 in an oblique way (the flowing direction of the air flow is shown by curved arrows in fig. 6), when the heat exchanger 100 is used as an evaporator, liquid drops condensed on the surfaces of fins or defrosting water has a component in the gravity direction, and the drainage performance of the heat exchanger 100 is improved. In addition, the length of the air duct 12 is lengthened due to the arrangement of the oblique corrugations, which is beneficial to improving the heat exchange efficiency of the heat exchanger 100.

When the corrugation on the tube fin unit 1 is non-oblique (i.e. α =0 °), the air duct 12 between two adjacent tube fin units 1 may extend in the horizontal direction.

In some exemplary embodiments, the sheet distance S between two adjacent tube fin units 1 is: s is more than or equal to 1.2mm and less than or equal to 1.6mm. Such as: the sheet spacing S may be: 1.3mm, 1.4mm, 1.5mm, etc.

The relationship between two adjacent tube fin monomers 1 is as follows: one tube fin unit 1 is rotated 180 degrees along a central line parallel to the refrigerant channel 113 to form an adjacent fin unit, and therefore, as shown in fig. 2, two tube fin units 1a and 1c spaced by one tube fin unit 1b are symmetrical, and the distance between the tube fin units 1a and 1c is kept the same at different positions, so that the fin pitch S can be set to be half of the distance between the tube fin units 1a and 1 c.

The distance between the tube fin units 1 can be determined according to the determined thickness of the fin parts 111, the number of the refrigerant channels 113 and the inner diameter of the refrigerant channels 113, and the distance between the tube fin units 1 can be selected to be proper under the condition that the wind resistance is not increased. The fin distance between the adjacent tube fin monomers 1 is set to be 1.2mm-1.6mm, so that the heat exchange capability of the heat exchanger 100 can be improved, and the wind resistance can be reduced.

In some exemplary embodiments, in the first direction, a distance between two adjacent abutment points of two adjacent fin units 1 is not greater than 7cm; in the first direction, among the multiple abutting points of the two adjacent tube fin units 1, the distance between the abutting point close to the first collecting pipe 2 and the first collecting pipe 2 is not more than 7cm, and the distance between the abutting point close to the second collecting pipe 3 and the second collecting pipe 3 is not more than 7cm.

When the heat exchanger 100 is 3D printed, if the fin unit 1 is not supported by being in contact with the adjacent fin unit 1 when the fin unit 1 is printed to a certain height, the fin unit 1 may topple. In this embodiment, along a first direction (i.e., a vertical direction when the heat exchanger is printed in a 3D manner), a distance between two adjacent abutting points of two adjacent fin units 1 is not greater than 7cm, and among the multiple abutting points of the two adjacent fin units 1, a distance between an abutting point close to the first collecting pipe 2 and the first collecting pipe 2 is not greater than 7cm, a distance between an abutting point close to the second collecting pipe 3 and the second collecting pipe 3 is not greater than 7cm, that is, a height difference between two adjacent contact points of the two adjacent fin units 1 is not greater than 7cm, a height difference between a contact point close to the first collecting pipe 2 and the first collecting pipe 2 of the two adjacent fin units 1 is not greater than 7cm, and a height difference between a contact point close to the second collecting pipe 3 and the second collecting pipe 3 of the two adjacent fin units 1 is not greater than 7cm. So set up and to guarantee when 3D prints heat exchanger 100, the pipe fin monomer 1 can not take place to empty, and still can guarantee that heat exchanger 100 can not take place to empty in the use pipe fin monomer 1.

Can pass through the wave length L of the corrugated sheet of the tube fin unit 1₂The corrugation direction is limited to ensure that the height difference between two adjacent contact points of two adjacent tube fin monomers 1, the height difference between the contact point of the two adjacent tube fin monomers 1 close to the first collecting pipe 2 and the first collecting pipe 2, and the height difference between the contact point of the two adjacent tube fin monomers 1 close to the second collecting pipe 3 and the second collecting pipe 3 are not more than 7cm, such as not more than 1cm, 2cm, 3cm, 4cm, 5cm, 6cm and the like. Wherein, the wave length L of the corrugated sheet of the tube fin monomer 1₂Comprises the following steps: l is more than or equal to 8mm₂Not more than 12mm, and the included angle alpha between the corrugation direction of the corrugated sheet of the tube fin monomer 1 and the first direction is as follows: when the angle alpha is more than or equal to 0 degree and less than 90 degrees, the height difference between two adjacent contact points of two adjacent tube fin monomers 1, the height difference between the contact point of the two adjacent tube fin monomers 1 close to the first collecting pipe 2 and the first collecting pipe 2, and the height difference between the contact point of the two adjacent tube fin monomers 1 close to the second collecting pipe 3 and the second collecting pipe 3 are not more than 7cm.

In an embodiment, the thickness of fin portion 111 is 0.2mm, and the internal diameter of refrigerant passageway 113 is 0.35mm, and the quantity of refrigerant passageway 113 is 4, and the piece distance between the pipe fin monomer 1 is 1.4mm, this moment the utility model discloses the heat exchanger 100 of embodiment compares in the finned tube heat exchanger 100 of volume production, and heat exchange efficiency promotes 12%, and the windage reduces 8%.

In some exemplary embodiments, the first header 2 and the second header 3 may take the form of square tubes or other forms, such as: round tubes, etc.

The utility model discloses heat exchanger 100, the heat transfer volume of heat exchanger is under the heat transfer difference such as, and is directly proportional with total heat transfer coefficient and outside of tubes heat transfer area, and the heat transfer theory is as follows:

heat exchange quantity Q = K.A₀·ΔT(1)

Air side heat transfer coefficient h₀＝(A_p+η·A_f)/A₀×h_a (3)

Wherein, A₀: air side heat exchange area; h is a total of_w: heat exchange coefficient of the inner side (refrigerant side) of the tube; a. The_p: tube heat exchange area; h is_a: the heat exchange coefficient of the outer side of the tube is not corrected; a. The_pi: refrigerant side heat exchange area; a. The_f: the heat exchange area of the fin part; a. The_co: the contact area of the fins with the tubes; eta: fin efficiency; h is_c: contact conductivity of the fins to the tubes; Δ T: the temperature difference.

In the formula (2), the first and second groups,

the thermal contact resistance of the fins and the tubes is higher, the total heat transfer coefficient K is smaller, and the heat exchange quantity is lower; in the embodiment of the present invention, the flow channel part 112 and the fin part 111 of the tube fin unit 1 are integrally formed, and there is no thermal contact resistance, so that the total heat transfer coefficient K is increased; in the formula (3), the larger the fin efficiency eta is, the larger the air side heat exchange coefficient h₀The larger the total heat transfer coefficient K is, the higher the heat exchange quantity of the heat exchanger 100 is, the utility model disclosesIn the embodiment, the fin efficiency η is about 1, and other finned tube heat exchangers are about 0.8-0.9, so the heat exchange capability of the heat exchanger 100 of the embodiment of the present invention is enhanced.

The embodiment of the utility model provides a still provide an air conditioner, including the heat exchanger 100 of any preceding embodiment.

The air conditioner includes an indoor unit and an outdoor unit, and the heat exchanger 100 may be disposed in the indoor unit and/or the outdoor unit.

In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and for simplicity of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or to implicitly indicate the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature.

In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless explicitly defined otherwise.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," and "fixed" are to be construed broadly and may, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be interconnected within two elements or in a relationship where two elements interact with each other unless otherwise specifically limited. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.

In the present invention, unless otherwise expressly stated or limited, the first feature may be directly on or directly under the second feature or indirectly on or directly in contact with the first or second feature through intervening media. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

In the description herein, references to the description of the term "one embodiment," some embodiments, "examples," "specific examples," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Moreover, various embodiments or examples and features of various embodiments or examples described in this specification can be combined and combined by one skilled in the art without being mutually inconsistent.

While embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations of the above embodiments may be made by those of ordinary skill in the art without departing from the scope of the present invention.

Claims (14)

1. A tube fin monomer is characterized by comprising a substrate, wherein the substrate is a corrugated sheet, the substrate comprises fin parts and flow channel parts which are alternately arranged, and a refrigerant channel is arranged in the flow channel part;

the refrigerant channel is bent and extended along a first direction, and an included angle alpha between the corrugation direction of the corrugated sheet and the first direction is as follows: alpha is more than or equal to 0 degree and less than 90 degrees.

2. A tube fin monomer according to claim 1, wherein α is 30 ° or more and 60 ° or less.

3. A tube fin unit according to claim 1 or 2, wherein a length L of the corrugated sheet is in a corrugation direction of the corrugated sheet₁To a single wavelength L₂The relationship between them is: 2 XL₂≤L₁≤5×L₂。

4. The tube fin unit according to claim 3, wherein L is less than or equal to 8mm₂≤12mm。

5. A tube fin unit according to claim 1 or 2, wherein the wave height H of the corrugated sheet is: h is more than or equal to 0.8mm and less than or equal to 1.6mm.

6. A tube fin unit according to claim 1 or 2, wherein the substrate is an integrally formed structure formed by a 3D metal printing process.

7. A tube fin unit according to claim 1 or 2, wherein the coolant passage has an inner diameter of not more than 0.4mm, and the fin portion has a thickness of not more than 0.4mm.

8. A heat exchanger, comprising: the pipe fin single body structure comprises a first collecting pipe, a second collecting pipe and a plurality of pipe fin single bodies as claimed in any one of claims 1 to 7, wherein the plurality of pipe fin single bodies are arranged in parallel, the wave bands, protruding towards each other, of two adjacent pipe fin single bodies are mutually abutted, one end of each pipe fin single body is connected with the first collecting pipe, and the other end of each pipe fin single body is connected with the second collecting pipe.

9. The heat exchanger as claimed in claim 8, wherein adjacent two of the fin units are symmetrically disposed about a line of symmetry parallel to the first direction along which the refrigerant channel extends.

10. The heat exchanger of claim 8, wherein the first header, the plurality of fin units, and the second header are a unitary structure formed by a 3D metal printing process, and the fin portions or the flow channel portions of the fin units are arranged to contact the fin portions or the flow channel portions of adjacent fin units; or

The first collecting pipe, the plurality of tube fin single bodies and the second collecting pipe are of a split type assembly structure, one end of each tube fin single body is connected with the first collecting pipe in an inserted mode, the other end of each tube fin single body is connected with the second collecting pipe in an inserted mode, and the fin portions of the two adjacent tube fin single bodies are in contact.

11. The heat exchanger according to any one of claims 8 to 10, wherein an air channel is formed between two adjacent fin units, and the air channel is gradually inclined downwards along the flowing direction of the wind.

12. The heat exchanger according to any one of claims 8 to 10, wherein a pitch S between adjacent two of the fin units is: s is more than or equal to 1.2mm and less than or equal to 1.6mm.

13. The heat exchanger according to any one of claims 8 to 10, wherein a distance between adjacent two abutting points of adjacent two of the fin units in the first direction is not more than 7cm;

in the first direction, among a plurality of abutting points of two adjacent tube fin monomers, the distance between the abutting point close to the first collecting pipe and the first collecting pipe is not more than 7cm, and the distance between the abutting point close to the second collecting pipe and the second collecting pipe is not more than 7cm.

14. An air conditioner characterized by comprising the heat exchanger of any one of claims 8 to 13.

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