REFRIGERANT DISTRIBUTING DEVICE AND HEAT EXCHANGER

- DANFOSS A/S

A refrigerant-distributing device and a heat exchanger comprising the refrigerant-distributing device are provided. The refrigerant-distributing device comprises a distributing tube (1) defining a first end and a second end in a length direction thereof and a plurality of nozzles (2) disposed on the distributing tube (1) along the length direction of the distributing tube, each nozzle having a predetermined length and being formed with a through-hole (21) communicating an interior of the distributing tube and an exterior of the distributing tube. By provision of the nozzles, the flow resistance is increased, and the refrigerant-flow rate is more uniform along the length direction of the distrusting tube. In addition, the refrigerant can be ejected along the radial direction, the axial direction, the circumferential direction, and other directions so that the uniformity of the refrigerant in the space outside the distributing tube is improved.

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Description
CROSS-REFERENCE TO RELATED APPLICATIONS

This is a “national phase” application of International Patent Application PCT/CN2011/073846 filed on May 9, 2011, which, in turn, is based upon and claims priority to Chinese Patent Application 201010590176.9 filed on Dec. 8, 2010.

BACKGROUND OF INVENTION

1. Field of Invention

The invention relates to a refrigerant-distributing, device of a heat exchanger and a heat exchanger comprising the refrigerant-distributing device.

2. Description of Related Art

A distributing tube is generally inserted into a header of the heat exchanger to ensure uniform distribution of a refrigerant in the heat-exchange tubes of the heat exchanger. The distributing tube is formed with openings through which the refrigerant enters into the header from the distributing tube to be distributed to individual heat-exchange tubes.

The conventional distributing tube has disadvantages. For example, in use, a refrigerant at an inlet of a heat exchanger is in a gaseous-liquid two-phase state, and the density difference between the gaseous refrigerant and the liquid refrigerant is large, which may cause gas-liquid separation, thus affecting the refrigerant-distribution uniformity. The gaseous-liquid refrigerant directly flows into the header through openings of the distributing tube, and the gas-liquid separation tends to occur when the gaseous-liquid refrigerant leaves the openings, thus affecting the refrigerant-distribution uniformity. Pressures at individual openings are not balanced in a refrigerant flow direction, thus causing flow-rate imbalance between individual openings in a length direction of the distributing tube. The machining of the openings is difficult due to the increased amount or different types of the openings, and the distributing tube is difficult to clean due to the burrs on machining surfaces of the openings.

The invention seeks to solve at least one of the problems existing in the related art.

SUMMARY OF INVENTION

Accordingly, an object of a first aspect of the invention is to provide a refrigerant-distributing device capable of improving the refrigerant-distribution uniformity.

An object of a second aspect of the invention is to provide a heat exchanger comprising the refrigerant-distributing device according to the first aspect of the invention that may have improved heat-exchange performance.

Embodiments of the first aspect of the invention provide a refrigerant-distributing device comprising: a distributing tube defining a first end and a second end in a length direction thereof and a plurality of nozzles disposed on the distributing tube along the length direction of the distributing tube, each nozzle having a predetermined length and being formed with as through-hole communicating an interior of the distributing tube and an exterior of the distributing tube.

The refrigerant-distributing device according to embodiments of the invention is capable of improving the flow-rate balance. The flow resistance is increased because of the nozzles, the pressures at individual nozzles may be balanced, and the pressure imbalance between individual nozzles may be reduced greatly so that the refrigerant-flow rate along the length direction of the distributing tube is more balanced.

The refrigerant-distributing device according to embodiments of the invention can control and adjust the flow direction of the refrigerant. The gaseous-liquid refrigerant may be ejected out of the nozzles along the radial direction, the axial direction, the circumferential direction, and other directions of the distributing tube so that the refrigerant-distribution uniformity in the exterior of the distributing tube is improved greatly.

In some embodiments, the plurality of nozzles are arranged in a plurality of rows in a circumferential direction of the distributing tube, and the nozzles in each row are arranged spirally.

In some embodiments, the through-hole is a circular hole and passes through inner and outer end surfaces of the nozzle, and a length of the through-hole is 0.125-250 times as large as a hydraulic diameter of the through-hole.

In some embodiments, the through-hole passes through inner and outer end surfaces of the nozzle, and an axial direction of the through-hole is inclined relative to an axial direction of the nozzle.

In some embodiments, the through-hole has a rectangular or cross-shaped cross-section.

In some embodiments, the through-hole defines a first through-hole segment extending in a radial direction of the nozzle and a second through-hole segment extending in an axial direction of the nozzle, an inner end of the second through-hole segment is communicated with the interior of the distributing tube, an outer end of the second through-hole segment is closed, and the first through-hole segment communicates the second through-hole segment with the exterior of the distributing tube.

In some embodiments, a plurality of the first through-hole segments are formed and arranged in a circumferential direction of the second through-hole segment.

In some embodiments, the through-hole defines a first through-hole segment and a second through-hole segment extending in an axial direction of the nozzle, an inner end of the second through-hole segment is communicated with the interior of the distributing tube, an outer end of the second through-hole segment is closed, the first through-hole segment communicates the second through-hole segment with the exterior of the distributing tube, and an axial direction of the first through-hole segment is deviated from a radial direction of the nozzle.

In some embodiments, an inner end of each nozzle is extended into the interior of the distributing tube by a predetermined length.

In some embodiments, the inner end of the each nozzle is formed with a bent portion.

In some embodiments, an inner end of each nozzle is flush with an inner wall surface or an outer wall surface of the distributing tube.

In some embodiments, the through-hole passes through inner and outer end surfaces of the nozzle, an axial direction of the through-hole is parallel with an axial direction of the nozzle, the distributing tube has a circular cross-section, a ratio H/D of a length H of the through-hole to a hydraulic diameter D of the distributing tube is in a range of 0.027-25, and a ratio H/L of the length H of the through-hole to a length L of the distributing tube is in a range of 3.3×10−4−0.125.

In some embodiments, a sum of cross-sectional areas of the through-holes of the nozzles is 0.01%-40% of a circumferential surface area of the distributing tube.

Embodiments according to the second aspect of the invention provide a heat exchanger comprising: an inlet header; an outlet header; a plurality of heat-exchange tubes each having two ends connected with the inlet header and the outlet header, respectively, to communicate the inlet header and the outlet header; a plurality of fins disposed between adjacent heat-exchange tubes, respectively; and a refrigerant-distributing device according to embodiments of the first aspect of the invention disposed in the inlet header.

Other objects, features, and advantages of the invention are readily appreciated as the invention becomes better understood while a subsequent detailed description of embodiments of the invention is read taken in conjunction with the accompanying drawing thereof.

BRIEF DESCRIPTION OF EACH FIGURE OF DRAWING OF INVENTION

FIG. 1 is a schematic view of a refrigerant-distributing device according to a first embodiment of the invention;

FIG. 2 is a top view of the refrigerant-distributing device shown in FIG. 1;

FIG. 3 is a schematic cross-sectional view of the refrigerant-distributing device shown in FIG. 1;

FIG. 4 is a partial sectional view of a refrigerant-distributing device according to a second embodiment of the invention;

FIG. 5 is a top view of the refrigerant-distributing device shown in FIG. 4;

FIG. 6 is a partial sectional view of a refrigerant-distributing device according to a third embodiment of the invention;

FIG. 7 is a top view of the refrigerant-distributing device shown in FIG. 6;

FIG. 8 is a schematic cross-sectional view of the refrigerant-distributing device shown in FIG. 6;

FIG. 9 is a partial sectional view of a refrigerant-distributing device according to a fourth embodiment of the invention;

FIG. 10 is a top view of the refrigerant-distributing device shown in FIG. 9;

FIG. 11 is a schematic cross-sectional view of the refrigerant-distributing device shown in FIG. 9;

FIG. 12 is a partial sectional view of a refrigerant-distributing device according to a fifth embodiment of the invention;

FIG. 13 is a top view of the refrigerant-distributing device shown in FIG. 12;

FIG. 14 is a schematic cross-sectional view of the refrigerant-distributing device shown in FIG. 12;

FIG. 15 is a schematic view of a refrigerant-distributing device according to a sixth embodiment of the invention;

FIG. 16 is a top view of the refrigerant-distributing device shown in FIG. 15;

FIG. 17 is a schematic cross-sectional view of the refrigerant-distributing device shown in FIG. 15;

FIG. 18 is a schematic view of a refrigerant-distributing device according to a seventh embodiment of the invention;

FIG. 19 is a top view of the refrigerant-distributing device shown in FIG. 18;

FIG. 20 is a schematic cross-sectional view of the refrigerant-distributing device shown in FIG. 18;

FIG. 21 is a schematic view of a refrigerant-distributing device according to an eighth embodiment of the invention;

FIG. 22 is a top view of the refrigerant-distributing device shown in FIG. 21;

FIG. 23 is a schematic cross-sectional view of the refrigerant-distributing device shown in FIG. 21;

FIG. 24 is a schematic view of a heat exchanger according to an embodiment of the invention;

FIG. 25 is a schematic partial cross-sectional view of an inlet header of the heat exchanger shown in FIG. 24; and

FIG. 26 is a graph illustrating a comparison between a “refrigerant distribution” effect of a refrigerant-distributing device according to an embodiment of the-invention and a “refrigerant distribution” effect of a conventional distributing tube.

 DETAILED DESCRIPTION OF EMBODIMENTS OF INVENTION

Reference will be made in detail to embodiments of the invention. The embodiments described herein with reference to the drawing are explanatory, illustrative, and used to generally understand the invention. The embodiments shall not be construed to limit the invention. The same or similar elements and the elements having same or similar functions are denoted by like reference numerals throughout the descriptions.

In the specification, unless specified or limited otherwise, relative terms such as “length direction,” “lateral,” “axial direction,” “upper,” “lower,” “front,” “rear,” “left,” “right,” “vertical,” “horizontal” “top,” “bottom,” “inner,” and “outer” as well as derivatives thereof (e.g., “horizontally,” “downwardly,” “upwardly,” etc.) should be construed to refer to the orientation as then described or as shown in the figure(s) under discussion. These relative terms are for convenience of description and do not require that the invention be constructed or operated in a particular orientation.

The refrigerant-distributing device according to embodiments of the invention will be described below with reference to the drawing.

As shown in FIGS. 1-23, the refrigerant-distributing device according to embodiments of the invention comprises a distributing tube 1 having a first end (i.e., the left end in FIG. 1) and a second end (i.e., the right end in FIG. 1) in a length direction (i.e., the left and right direction in FIG. 1) thereof. A plurality of nozzles 2 are disposed on the distributing tube 1 along the length direction of the distributing tube 1, and each nozzle 2 has a predetermined length and is formed with a through-hole 21 communicating an interior of the distributing tube 1 and an exterior of the distributing tube 1. Here, a person having ordinary skill in the related art will appreciate that the exterior of the distributing tube 1 means an interior of a header when the refrigerant-distributing device is mounted into the header of a heat exchanger.

In an example, as shown in FIG. 1, the first end of the distributing tube 1 is open, and the second end of the distributing tube 1 is closed. However, a person having ordinary skill in the related art will appreciate that the second end of the distributing tube 1 may be open and then closed by an end wall of the header when the refrigerant-distributing device is mounted into the header of the heat exchanger. To facilitate description, hereinafter, the left end of the distributing tube 1 is referred as an “inlet end” of the distributing tube 1 (that is, the left-end opening of the distributing tube 1 is used as the refrigerant inlet of the distributing tube 1).

With the refrigerant-distributing device according to embodiments of the invention, the plurality of nozzles 2 are mounted on the distributing tube 1 along the length direction of the distributing tube 1, and the “pumping” effect may be generated in the nozzles 2 under the same pressure as that in the related art such that the flow rate in the nozzles 2 is larger than that in openings of a conventional distributing tube when the hydraulic diameter of the nozzle 2 is identical with that of the opening of the conventional distributing tube.

In addition, the gaseous refrigerant and the liquid refrigerant may be mixed again when flowing in the through-holes 21 of the nozzles 2, thus further reducing the gas-liquid separation. Moreover, the through-holes 21 of the nozzles 2 may increase the length of the refrigerant-ejection passage-so-as to increase the refrigerant-distribution-pressure difference such that the refrigerant flow-rate distribution is more uniform along the entire length direction of the distributing tube 1, thus improving the heat-exchange performance of the heat exchanger.

By comparison to the conventional distributing tube having distributing openings formed in a wall thereof with the refrigerant-distributing device according to embodiments of the invention, the nozzles 2 each having a predetermined length are disposed on the distributing tube 1. The refrigerant-flow rate Q follows a formula:


Q=μ0A√{square root over (2gH)},

where A is a cross-sectional area of the through-hole 21 of the nozzle 2, H is a pressure head, g is the gravity acceleration, and μ0 is a flow-rate coefficient. Because the flow-rate coefficient μ0 of the nozzle 2 is 0.82 and the flow-rate coefficient μ0 of the opening in the conventional distributing tube is 0.62, the flow rate in the nozzle 2 is larger than that in the opening in the conventional distributing tube when the hydraulic diameter of the nozzle 2 is identical with that of the opening in the conventional distributing tube.

In addition, with the conventional distributing tube, the refrigerant flows out of the distributing tube through individual openings formed in the wall of the distributing tube, the pressure drops in the individual openings are unequal, and a pressure difference between the refrigerant inlet and the opening farthest from the refrigerant inlet (i.e., the last opening) differs greatly from that between the refrigerant inlet and the opening nearest to the refrigerant inlet (i.e., the first opening) such that the refrigerant flow-rate distribution along a length direction of the distributing tube is non-uniform (that is, the flow rate in the first opening is much larger than that in the last opening). In contrast, with the refrigerant-distributing device according to embodiments of the invention, because the nozzles 2 each having a predetermined length are disposed on the distributing tube 1, the refrigerant-flow passage in each nozzle 2 is lengthened, and the refrigerant-distribution-pressure drop in the nozzles 2 is larger than that in the openings in the conventional distributing tube such that a pressure difference between the refrigerant inlet and the first nozzle 2 (for example, the left-most nozzle in FIG. 1) is substantially identical with a pressure difference between the refrigerant inlet and the last nozzle 2 (for example, the right-most nozzle in FIG. 1). Therefore, the refrigerant distribution along the length direction of the distributing tube 1 is more uniform, as shown in FIG. 26. In FIG. 26, the abscissas s represent a distance from each opening in the conventional distributing tube to the refrigerant inlet and a distance from each nozzle 2 in the refrigerant-distributing device according to embodiments of the invention to the refrigerant inlet, and the ordinates in represent a refrigerant-flow rate in each opening and a refrigerant-flow rate in each nozzle 2.

The refrigerant-distributing device according to a first embodiment of the invention will be described below with reference to FIGS. 1-3. As shown in FIGS. 1-3, with the refrigerant-distributing device according to the first embodiment of the invention, the plurality of nozzles 2 are disposed on the distributing tube 1 along the length direction (i.e., the left and right direction in FIG. 1) of the distributing tube 1 and arranged on the distributing tube 1 in a straight line. In an embodiment, the distributing tube 1 is formed with a plurality of mounting holes 11, and each nozzle 2 is fitted and mounted in one mounting hole 11.

In the embodiment shown in FIGS. 1-3, each nozzle 2 is cylindrical, and the through-hole 21 is a circular hole and passes through an inner end surface (e.g., the lower end surface in FIG. 1) and an outer end surface (e.g., the upper end surface in FIG. 1) of the nozzle 2. A length of the through-hole 21 is 0.125-250 times as large as a hydraulic diameter of the through-hole 21. It should be noted that if the length of the through-hole 21 of the nozzle 2 is too large, the flow resistance of the refrigerant in the nozzle 2 will be increased; and, if the length of the through-hole 21 of the nozzle 2 is too small, the “pumping” effect will be weakened. Therefore, it has been found that the balance between reducing the resistance and maintaining the “pumping” effect may be achieved by controlling the length of the through-hole 21 to be 0.125-250 times as large as the hydraulic diameter of the through-hole 21.

As shown in FIGS. 1-3, in some specific examples, an outer end (i.e., the upper end in FIG. 1) of the through-hole 21 has an enlarged segment 22, thus facilitating the machining of the through-hole 21.

As shown in FIGS. 1-2, in some examples, the plurality of nozzles 2 are spaced apart from each other at equal intervals in the length direction of the distributing tube 1. However, the invention is not limited to this. For example, the plurality of nozzles 2 may be spaced apart from each other at unequal intervals.

As shown in FIG. 3, in one example, an axial direction of the through-hole 21 is consistent with an axial direction of the nozzle 2.

In other examples, an inner end (i.e., the end of each nozzle 2 close to the distributing tube 1) of each nozzle 2 is extended into the interior of the distributing tube 1 by a predetermined length. Because the nozzle 2 is inserted into the interior of the distributing tube 1, the refrigerant is agitated when flowing in the distributing tube 1 along the axial direction of the distributing tube 1, and the gaseous refrigerant and the liquid refrigerant are separated from and then remixed with each other continuously such that the gaseous refrigerant and the liquid refrigerant may be still mixed uniformly when flowing to a region in the distributing tube 1 away from the refrigerant inlet of the distributing tube 1. Alternatively, the inner end of each nozzle 2 is flush with the inner wall surface or the outer wall surface of the distributing tube 1.

In some embodiments, the through-hole 21 passes through the inner end surface and the outer end surface of the nozzle 2, and the axial direction of the through-hole 21 is parallel with the axial direction of the nozzle 2. The distributing tube 1 is a circular tube, a ratio H/D of a length H of the through-hole 21 to a hydraulic diameter D of the distributing tube 1 is in a range of 0.027-25, and a ratio of the length of the through-hole 21 to a length L of the distributing tube 1 is in a range of 3.3×10−4−0.125.

According to some embodiments of the invention, if the local pressure drop is not considered, according to a formula of the frictional resistance (i.e., frictional drag in the distributing tube:


ΔP=λ(1/d)ρμ2/2,

the resistance in a single nozzle is:


ΔPnozzle=λ1(H/d)ρμ2i/2,

the frictional resistance in the distributing tube is:


ΔPtube=λ2(L/D)ρμ2/2,

when ΔPnozzle is larger than ΔPtube, the optimization of the flow rate in the nozzle may be realized.

Therefore, when the ratio H/D of the length H of the through-hole 21 to the hydraulic diameter D of the distributing tube 1 is in a range of 0.027-25 and the ratio H/L of the length H of the through-hole 21 to the length L of the distributing tube 1 is in a range of 3.3×10−4−0.125, the flow-rate distribution between individual nozzles 2 of the distributing tube 1 may be optimized. For example, in a specific example, H=1-25 millimeters, d=0.1-8 millimeters, D=1-36 millimeters, and L=0.2-3 meters.

Likewise, based on the above analysis, when a sum of cross-sectional areas of the through-holes 21 of the nozzle 2 is 0.01%-40% of a circumferential-surface area of the distributing tube 1, the flow-rate distribution between individual nozzles 2 of the distributing tube 1 may be optimized.

In the embodiment shown in FIGS. 1-3, the distributing tube 1 has a circular cross-section, and the through-hole 21 in the nozzle 2 is a circular hole (i.e., the through-hole has a circular cross-section). However, the invention is not limited to this. For example, in other embodiments, the distributing tube 1 may have a rectangular cross-section, and the cross-section of the through-hole 21 may have a square shape or any other suitable shape.

The refrigerant-distributing device according to a second embodiment of the invention will be described below with reference to FIGS. 4-5. In the second embodiment shown in FIGS. 4-5, the nozzle 2 is cylindrical, the through-hole 21 has a circular cross-section, the through-hole 21 passes through an inner end surface (i.e., a lower end surface in FIG. 4) and an outer end surface (i.e., an upper end surface in FIG. 4) of the nozzle 2, and the axial direction of the through-hole 21 is inclined at a predetermined angle α of, for example, about 0-90 degrees (in an embodiment, 0-60 degrees) relative to the axial direction of the nozzle 2. By controlling the axial direction of the through-hole 21 to be inclined relative to the axial direction of the nozzle 2, the length of the through-hole 21 may be increased without changing the length of the nozzle 2. Therefore, the length of the refrigerant-flow passage may be increased to enhance the “mixing” effect of the gaseous refrigerant and the liquid refrigerant, and the direction of the refrigerant-flow passage may be changed so that the refrigerant is ejected out of the distributing tube 1 at a particular angle to improve the “distribution” effect.

The refrigerant-distributing device according to a third embodiment of the invention will be described below with reference to FIGS. 6-8. In the third embodiment shown in FIGS. 6-8, the nozzle 2 is cylindrical, the through-hole 21 passes through an inner end surface and an outer end surface of the nozzle 2, and the through-hole 21 has a cross-shaped cross-section. However, the invention is not limited to this. For example, the through-hole 21 may have a rectangular cross-section. Since the through-hole 21 has a non-circular cross-section, the “pumping” effect and the “ejection” effect may be further enhanced, and the gas-liquid separation may be eliminated.

The refrigerant-distributing device according to a fourth embodiment of the invention will be described below with reference to FIGS. 9-11. In the fourth embodiment shown in FIGS. 9-11, the inner end of each nozzle 2 is extended into the interior of the distributing tube 1 by a predetermined length, and the inner end of the each nozzle 2 is formed with a bent portion. In other words, the nozzle 2 may be of a bent cylinder. An angle β between the bent portion and the main body of the nozzle 2 may be in a range of about 45 degrees-180 degrees. By forming the bent portion at the inner end of the nozzle 2, the gaseous refrigerant and the liquid refrigerant may be guided, and the “agitation” effect on the refrigerant in the distributing tube 1 may be further enhanced.

The refrigerant-distributing device according to a fifth embodiment of the invention will be described below with reference to FIGS. 12-14. In the fifth embodiment shown in FIGS. 12-14, the through-hole 21 defines a first through-hole segment 212 extending in a radial direction of the nozzle 2 and a second through-hole segment 211 extending in an axial direction of the nozzle 2. The inner end (the lower end in FIG. 12) of the second through-hole segment 211 is communicated with the interior of the distributing tube 1, and the outer end the upper end in FIG. 12) of the second through-hole segment 211 is closed. The first through-hole segment 212 communicates the second through-hole segment 211 with the exterior of the distributing tube 1. In other words, the inner end of the first through-hole segment 212 is communicated with the second through-hole segment 211, and the outer end of the first through-hole segment 212 is communicated with the exterior of the distributing tube 1. In a specific example, a plurality of the first through-bole segments 212 (for example, 2-12 first through-hole segments 212) are formed and arranged in the circumferential direction of the second through-hole segment 211. Since the first through-hole segment 212 is extended in the radial direction of the nozzle 2, the refrigerant is easy to control to be ejected out of the nozzle 2 along various radial directions of the nozzle 2, but may not be ejected along the radial direction of the distributing tube 1, thus improving the distribution uniformity of the refrigerant in the exterior of the distributing tube 1. Therefore, the refrigerant may be distributed in the exterior of the distributing tube 1 more uniformly.

The refrigerant-distributing device according to a sixth embodiment of the invention will be described below with reference to FIGS. 15-17. In the sixth embodiment shown in FIGS. 15-17, the through-hole 21 defines a plurality of first through-hole segments 212 and a second through-hole segment 211 extending in an axial direction of the nozzle 2. The inner end of the second through-hole segment 211 is communicated with the interior of the distributing tube 1, and the outer end of the second through-hole segment 211 is closed. The first through-hole segments 212 communicate the second through-hole segment 211 with the exterior of the distributing tube 1. In the embodiment shown in FIGS. 15-17, the first through-hole segments 212 and the second through-hole segment 211 have circular cross-sections, and the axial direction of the first through-hole segment 212 is deviated from the radial direction of the nozzle 2 (for example, the axial direction of the first through-hole segment 212 is consistent with a tangential direction of the second through-hole segment 211). Therefore, the refrigerant passing through the first through-hole segment 212 is ejected along a direction deviated from the radial direction of the nozzle 2, and, consequently, the rotation of the refrigerant after being ejected into the second through-hole segment 212 is enhanced, thus improving the distribution uniformity of the refrigerant in the exterior of the distributing tube 1. Therefore, the gaseous refrigerant and the liquid refrigerant may be distributed in the exterior of the distributing tube 1 more uniformly.

The refrigerant-distributing device according to a seventh embodiment of the invention will be described below with reference to FIGS. 18-20. In the seventh embodiment shown in FIGS. 18-20, the through-bole 21 defines a first through-hole segment 212 and a second through-hole segment 211 extending in an axial direction of the nozzle 2. The first through-hole segment 212 and the second through-hole segment 211 have rectangular cross-sections. Alternatively, a plurality of first through-hole segments 212 may be formed and extended in the radial direction of the nozzle 2 or a direction deviated from the radial direction of the nozzle 2.

The refrigerant-distributing device according to an eighth embodiment of the invention will be described below with reference to FIGS. 21-23. In the eighth embodiment shown in FIGS. 21-23, the plurality of nozzles 2 are spirally arranged in the length direction of the distributing tube 1. Therefore, the gaseous refrigerant and the liquid refrigerant may be spirally ejected along the length direction of the distributing tube 1 so that the gaseous refrigerant and the liquid refrigerant may be uniformly distributed in the exterior of the distributing tube 1.

In the above embodiments, the plurality of nozzles 2 are arranged in one row. However, it should be appreciated that the plurality of nozzles 2 may be arranged in a plurality of rows in a circumferential direction of the distributing tube 1 and the nozzle 2 in each row may be arranged spirally or linearly.

In the above embodiments, the nozzles 2 are cylindrical. However, the-invention is not limited to this. For example, the nozzles 2 may be of a prism having a rectangular cross-section or a cross-section of other shapes.

In some embodiments, the nozzles 2 may be manufactured separately and mounted onto the distributing tube 1. Alternatively, the nozzles 2 and the distributing tube 1 may be integrally manufactured (for example, the nozzles 2 and the distributing tube 1 are integrally cast).

With the refrigerant-distributing device according to embodiments of the invention, because the nozzles 2 are disposed on the distributing tube 1, the “distribution” effect may be improved, and the separation of the gaseous refrigerant and the liquid refrigerant may be reduced, thus improving the “heat exchange” effect.

The heat exchanger according to an embodiment of the invention will be described below with reference to FIGS. 24-25. As shown in FIGS. 24-25, the heat exchanger according to an embodiment of the invention comprises an inlet header 100, an outlet header 200, a plurality of heat-exchange tubes 300, a plurality of fins 400, and a refrigerant-distributing device described with reference to embodiments of the invention.

Two ends of each heat-exchange tube 300 are connected with the inlet header 100 and the outlet header 200, respectively, to communicate the inlet header 100 and the outlet header 200. The plurality of fins 400 are disposed between adjacent heat-exchange tubes 300, respectively. The refrigerant-distributing device is disposed in the inlet header 100. As shown in FIGS. 24-25, one end (i.e., a right end in FIG. 24) of the distributing tube 1 of the refrigerant-distributing device is inserted into the inlet header 100 along a length direction of the inlet header 100. For example, the one end of the distributing tube 1 may be closed by a separate end cap or the right-end wall of the inlet header 100. The other end (i.e., a left end in FIG. 24) of the distributing tube 1 may be exposed out of the inlet header 100 and used as a refrigerant inlet of the heat exchanger. With the heat exchanger according to an embodiment of the invention, the “refrigerant distribution” effect and the heat-exchange performance are good.

It should be appreciated that, in some embodiments, the refrigerant-distributing device according to an embodiment of the invention may also be disposed in the outlet header 200. In this case, the refrigerant-distributing device is used as a refrigerant-collecting device. Alternatively, the refrigerant-distributing device according to an embodiment of the invention may be disposed in the inlet header 100 and the outlet header 200 simultaneously.

In conclusion, the refrigerant-distributing device and the heat exchanger according to embodiments of the invention are capable of improving the flow-rate balance. Since the flow resistance is increased by the through-holes of the nozzles, the pressure difference between individual nozzles may be balanced, and the pressure imbalance between individual nozzles may be reduced largely so that the refrigerant-flow rate along the length direction of the distributing tube may be more balanced.

The refrigerant-distributing device and the heat exchanger according to embodiments of the invention are capable of controlling and adjusting the direction of the refrigerant. The gaseous refrigerant and the liquid refrigerant may be ejected out of the nozzles not only along the radial direction of the distributing tube, but also along the axial direction, the circumferential direction, or other directions of the distributing tube so that the refrigerant-distribution uniformity in the exterior of the distributing tube may be improved largely.

Reference throughout this specification to “a first embodiment,” “a second embodiment,” “some embodiments,” “an example,” “a specific example,” or “some examples” means 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. Thus, the appearances of the above phrases in various places throughout this specification are not necessarily referring to the same embodiment or example of the invention. Furthermore, the particular features, structures, materials, or characteristics may be combined in any suitable manner in one embodiment or example or more embodiments or examples.

Although explanatory embodiments have been shown and described, it would be appreciated by those skilled in the related art that the above embodiments cannot be construed to limit the invention, and changes, alternatives, and modifications can be made in the embodiments without departing from the spirit, principles, and scope of the invention.

Claims

1. A refrigerant-distributing device comprising:

a distributing tube defining a first end and a second end in a substantially length direction thereof; and
a plurality of nozzles disposed on the distributing tube along the length direction of the distributing tube, wherein each of the nozzles defines a predetermined length and is formed with a through-hole communicating an interior of the distributing tube and an exterior of the distributing tube.

2. The refrigerant-distributing device according to claim 1, wherein the nozzles are arranged in a plurality of rows in a substantially circumferential direction of the distributing tube and the nozzles in each of the rows are arranged substantially spirally.

3. The refrigerant-distributing device according to claim 1, wherein the through-hole is substantially circular and passes through inner and outer end surfaces of the nozzle and a length of the through-hole is about 0.125-about 250 times as large as a hydraulic diameter of the through-hole.

4. The refrigerant-distributing device according to claim 1, wherein the through-hole passes through inner and outer end surfaces of the nozzle and a substantially axial direction of the through-hole is inclined relative to a substantially axial direction of the nozzle.

5. The refrigerant-distributing device according to claim 1, wherein the through-hole defines either of a substantially rectangular and cross-shaped cross-section.

6. The refrigerant-distributing device according to claim 1, wherein the through-hole defines a first through-hole segment extending in a substantially radial direction of the nozzle and a second through-hole segment extending in a substantially axial direction of the nozzle an inner end of the second through-hole segment is communicated with the interior of the distributing tube, an outer end of the second through-hole segment is closed and the first through-hole segment communicates the second through-hole segment with the exterior of the distributing tube.

7. The refrigerant-distributing device according to claim 6, wherein a plurality of the first through-hole segments are formed and arranged in a substantially circumferential direction of the second through-hole segment.

8. The refrigerant-distributing device according to claim 1, wherein the through-hole defines a first through-hole segment and a second through-hole segment extending in a substantially axial direction of the nozzle an inner end of the second through-hole segment is communicated with the interior of the distributing tube, an outer end of the second through-hole segment is closed the first through-hole segment communicates the second through-hole segment with the exterior of the distributing tube, and a substantially axial direction of the first through-hole segment is deviated from a substantially radial direction of the nozzle.

9. The refrigerant-distributing device according to of claim 1, wherein an inner end of each of the nozzles is extended into the interior of the distributing tube by a predetermined length.

10. The refrigerant-distributing device according to claim 9, wherein the inner end of the nozzle is formed with a bent portion.

11. The refrigerant-distributing device according to claim 1, wherein an inner end of each of the nozzles is substantially flush with either of an inner wall surface and an outer wall surface of the distributing tube.

12. The refrigerant-distributing device according to claim 1, wherein the through-hole passes through inner and outer end surfaces of the nozzle a substantially axial direction of the through-hole is substantially parallel with a substantially axial direction of the nozzle, the distributing tube defines a substantially circular cross-section, a ratio H/D of a length H of the through-hole to a hydraulic diameter D of the distributing tube is in a range of about 0.027 to about 25, and a ratio H/L of the length H of the through-hole to a length L of the distributing tube is in a range of about 3.3×10−4 to about 0.125.

13. The refrigerant-distributing device according to claim 1, wherein a sum of cross-sectional areas of the through-holes of the nozzles is about 0.01% to about 40% of a substantially circumferential-surface area of the distributing tube.

14. A heat exchanger comprising:

an inlet header;
an outlet header;
a plurality of heat-exchange tubes each of which defines two ends connected with the inlet header and the outlet header, respectively, to communicate the inlet header and the outlet header;
a plurality of fins disposed between adjacent heat-exchange tubes, respectively; and
a refrigerant-distributing device disposed in the inlet header and including: a distributing tube defining a first end and a second end in a substantially length direction thereof; and a plurality of nozzles disposed on the distributing tube along the length direction the distributing tube, wherein each of the nozzles defines a predetermined length and is formed with a through-hole communicating an interior of the distributing tube and an exterior of the distributing tube.

15. The heat exchanger according to claim 14, wherein the nozzles are arranged in a plurality of rows in a substantially circumferential direction of the distributing tube and the nozzles in each of the rows are arranged substantially spirally.

16. The heat exchanger according to claim 14, wherein the through-hole is a substantially circular and passes through inner and outer end surfaces of the nozzle and a length of the through-hole is about 0.125-about 250 times as large as a hydraulic diameter of the through-hole.

17. The heat exchanger according to claim 14, wherein the through-hole passes through inner and outer end surfaces of the nozzle and a substantially axial direction of the through-hole is inclined relative to a substantially axial direction of the nozzle.

18. The heat exchanger according to claim 14, wherein the through-hole defines either of a rectangular and cross-shaped cross-section.

19. The heat exchanger according to claim 14, wherein the through-hole defines a first through-hole segment extending in a substantially radial direction of the nozzle and a second through-hole segment extending in a substantially axial direction of the nozzle an inner end of the second through-hole segment is communicated with the interior of the distributing tube, an outer end of the second through-hole segment is closed, and the first through-hole segment communicates the second through-hole segment with the exterior of the distributing tube.

20. The heat exchanger according to claim 19, wherein a plurality of the first through-hole segments are formed and arranged in a substantially circumferential direction of the second through-hole segment.

Patent History
Publication number: 20130312944
Type: Application
Filed: May 9, 2011
Publication Date: Nov 28, 2013
Applicants: DANFOSS A/S (NORDBORG), SANHUA HOLDING GROUP CO LTD (ZHEIJANG)
Inventors: Qiang Gao (Hangzhou), Yanxing Li (Hangzhou), Ningjie Huang (East Amherst, NY)
Application Number: 13/992,002
Classifications
Current U.S. Class: Inlet And Outlet Header Means (165/175); With Discrete Heat Transfer Means (165/181)
International Classification: F28F 1/12 (20060101);