WO2012075772A1 - 制冷剂分配装置和具有它的换热器 - Google Patents

制冷剂分配装置和具有它的换热器 Download PDF

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Publication number
WO2012075772A1
WO2012075772A1 PCT/CN2011/073846 CN2011073846W WO2012075772A1 WO 2012075772 A1 WO2012075772 A1 WO 2012075772A1 CN 2011073846 W CN2011073846 W CN 2011073846W WO 2012075772 A1 WO2012075772 A1 WO 2012075772A1
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WO
WIPO (PCT)
Prior art keywords
hole
nozzle
refrigerant
distribution device
refrigerant distribution
Prior art date
Application number
PCT/CN2011/073846
Other languages
English (en)
French (fr)
Inventor
高强
李艳星
黄宁杰
Original Assignee
三花丹佛斯（杭州）微通道换热器有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三花丹佛斯（杭州）微通道换热器有限公司 filed Critical 三花丹佛斯（杭州）微通道换热器有限公司
Priority to EP11846143.3A priority Critical patent/EP2650635B1/en
Priority to JP2013541187A priority patent/JP6114995B2/ja
Priority to US13/992,002 priority patent/US20130312944A1/en
Publication of WO2012075772A1 publication Critical patent/WO2012075772A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/14—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means with multiple outlet openings; with strainers in or outside the outlet opening
    • B05B1/20—Arrangements of several outlets along elongated bodies, e.g. perforated pipes or troughs, e.g. spray booms; Outlet elements therefor
    • B05B1/202—Arrangements of several outlets along elongated bodies, e.g. perforated pipes or troughs, e.g. spray booms; Outlet elements therefor comprising inserted outlet elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/34—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl
    • B05B1/3405—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl

Definitions

  • the present invention relates to a refrigerant distribution device for a heat exchanger and a heat exchanger having the same. Background technique
  • a distribution pipe is usually inserted into the manifold of the heat exchanger, and an opening is provided in the distribution pipe, and the refrigerant passes through the opening from the distribution pipe into the collecting pipe to be distributed to Inside each heat exchange tube.
  • the refrigerant state at the inlet of the heat exchanger is a gas-liquid two-phase state. Since the density of the gas phase refrigerant and the liquid phase refrigerant are largely different, gas-liquid separation phenomenon occurs. Thereby affecting the distribution uniformity of the distributed refrigerant. Since the gas-liquid two-phase refrigerant directly flows out from the opening of the surface of the distribution pipe and enters the header, the gas-liquid two-phase refrigerant is liable to cause gas-liquid separation when leaving the opening, which affects the uniformity of distribution.
  • the present invention aims to solve at least one of the technical problems existing in the prior art.
  • An object of the second aspect of the present invention is to provide a heat exchanger having the refrigerant distributing device according to the first aspect of the present invention, which heat exchanger has improved heat exchange performance.
  • a refrigerant distribution device includes: a distribution pipe defining first and second ends in a longitudinal direction thereof, wherein the distribution pipe is provided with a plurality of nozzles along the length direction Each nozzle has a predetermined length and is formed with a through hole that communicates the inner cavity of the distribution tube with the outside.
  • the refrigerant distribution device has the ability to improve the flow balance, and the flow resistance is increased due to the nozzle, so that the pressure relationship between the nozzles can be balanced, so that the pressure between the nozzles is unbalanced. It is greatly reduced, so that the refrigerant flow rate along the length of the distribution pipe is more balanced.
  • the refrigerant distribution device has a direction control and adjustment capability, and the refrigerant gas-liquid two phases can be sprayed not only along the radial direction of the distribution pipe but also along the distribution pipe when being sprayed out of the nozzle. Spraying in the axial, circumferential or other directions can greatly improve the spatial refrigerant non-uniformity outside the distribution pipe.
  • the refrigerant distribution device may further have the following additional technical features: the plurality of nozzles are arranged in a plurality of rows in the circumferential direction of the distribution pipe, wherein the nozzles in each row are spirally arrangement.
  • the through hole is a circular hole and extends through the inner end surface and the outer end surface of the nozzle, wherein the length of the through hole is 0.125-250 times the diameter of the through hole.
  • the through hole penetrates the inner end surface and the outer end surface of the nozzle, and an axial direction of the through hole is inclined with respect to an axial direction of the nozzle.
  • the through hole is a rectangular slot or a cross slot.
  • the through hole includes a first through hole portion extending radially along the nozzle and a second through hole portion extending axially along the nozzle, wherein an inner end of the second through hole portion and a lumen of the distribution tube In communication, the outer end of the second through hole portion is closed, and the first through hole portion communicates the second through hole portion with the outside.
  • the first through hole portion is plural, and the plurality of first through hole portions are arranged along a circumferential direction of the second through hole portion.
  • the through hole includes a first through hole portion and a second through hole portion extending axially along the nozzle, wherein an inner end of the second through hole portion communicates with a lumen of the distribution tube, the second pass The outer end of the hole portion is closed, and the first through hole portion communicates the second through hole portion with the outside, and the axial direction of the first through hole portion is offset from the radial direction of the nozzle.
  • each nozzle extends into the lumen of the dispensing tube a predetermined distance.
  • the inner end of the nozzle is formed with a bent portion.
  • each nozzle is flush with the inner or outer wall of the dispensing tube.
  • the through hole penetrates the inner end surface and the outer end surface of the nozzle, and the axial direction of the through hole is parallel to the axial direction of the nozzle, and the distribution tube is a circular tube, wherein the length H of the through hole is The ratio of the ratio H/D of the water tube diameter of the distribution tube is in the range of 0. 027-25 and the ratio of the length H of the through hole to the length L of the distribution tube is 3. 3 X 10 - 4 -0 Within the range of 125.
  • a heat exchanger including: an inlet header; an outlet header; a heat exchange tube, two ends of the heat exchange tube and an inlet header and an outlet manifold, respectively
  • the tubes are connected to communicate the inlet header and the outlet header; the fins are respectively disposed between the adjacent heat exchange tubes; and the refrigerant distribution device, the refrigerant distribution device to the inlet set
  • Figure 1 is a schematic view of a refrigerant distribution device according to a first embodiment of the present invention
  • Figure 2 is a plan view of the refrigerant distribution device shown in Figure 1;
  • Figure 3 is a schematic cross-sectional view of the refrigerant distribution device of Figure 1;
  • Figure 4 is a partial cross-sectional view showing a refrigerant distribution device according to a second embodiment of the present invention;
  • Figure 5 is a plan view of the refrigerant distribution device shown in Figure 4.
  • Figure 6 is a partial cross-sectional view showing a refrigerant distribution device according to a third embodiment of the present invention.
  • Figure 7 is a plan view of the refrigerant distribution device shown in Figure 6;
  • Figure 8 is a schematic cross-sectional view of the refrigerant distribution device shown in Figure 6;
  • Figure 9 is a partial cross-sectional view showing a refrigerant distribution device according to a fourth embodiment of the present invention.
  • Figure 10 is a plan view of the refrigerant distribution device shown in Figure 9;
  • Figure 11 is a schematic cross-sectional view of the refrigerant distribution device shown in Figure 9;
  • Figure 12 is a partial cross-sectional view showing a refrigerant distribution device according to a fifth embodiment of the present invention.
  • Figure 13 is a plan view of the refrigerant distribution device shown in Figure 12;
  • Figure 14 is a schematic cross-sectional view of the refrigerant distribution device shown in Figure 12;
  • Figure 15 is a schematic view of a refrigerant distribution device according to a sixth embodiment of the present invention.
  • Figure 16 is a plan view of the refrigerant distribution device shown in Figure 15;
  • Figure 17 is a schematic cross-sectional view of the refrigerant distribution device shown in Figure 15;
  • Figure 18 is a schematic view of a refrigerant distribution device according to a seventh embodiment of the present invention.
  • Figure 19 is a plan view of the refrigerant distribution device shown in Figure 18;
  • Figure 20 is a schematic cross-sectional view of the refrigerant distribution device shown in Figure 18;
  • Figure 21 is a schematic view of a refrigerant distribution device according to an eighth embodiment of the present invention.
  • Figure 22 is a plan view of the refrigerant distribution device shown in Figure 21;
  • Figure 23 is a schematic cross-sectional view of the refrigerant distribution device shown in Figure 21;
  • FIG. 24 is a schematic illustration of a heat exchanger in accordance with an embodiment of the present invention.
  • Figure 25 is a partial cross-sectional view showing the inlet header of the heat exchanger shown in Figure 24;
  • Fig. 26 is a graph showing a comparison of the effect of the distribution of the refrigerant to the refrigerant distribution device of the embodiment of the present invention and the distribution effect of the conventional distribution pipe to the refrigerant. detailed description
  • a refrigerant distribution device includes a distribution pipe 1 which defines a first end in its longitudinal direction (left-right direction in FIG. 1) (left end in FIG. 1) And the second end (the right end in Fig. 1), the dispensing tube 1 is provided with a plurality of nozzles 2 along its length, each nozzle 2 having a predetermined length and formed with a through hole 21, the through hole 21 will be a distribution tube
  • the inner cavity of 1 is in communication with the outside.
  • the outside refers to the outside of the nozzle 2 and the distribution pipe 1, for example, when the refrigerant distribution device of the embodiment of the present invention is installed in the header of the heat exchanger, the outside refers to the header.
  • the inner cavity when the refrigerant distribution device of the embodiment of the present invention is installed in the header of the heat exchanger, the outside refers to the header.
  • the first end of the dispensing tube 1 is open and the second end is closed, however, it will be understood that the second end of the dispensing tube 1 can be open, for example, can be installed When it is inside the collector of the heat exchanger, it is closed by the end face of the collecting pipe.
  • the left end of the distribution pipe 1 is referred to as the inlet end of the distribution pipe, that is, the left end opening of the distribution pipe 1 is the refrigerant inlet of the distribution pipe 1.
  • the nozzle 2 since the nozzle 2 is provided along the longitudinal direction of the distribution pipe 1, a pumping effect can be formed in the nozzle 2 under the same pressure, thereby being the same At the hydraulic diameter, the nozzle 2 provides a greater flow rate than the opening in a conventional dispensing tube.
  • the gas-liquid two-phase refrigerant can be remixed during the flow of the refrigerant through the through holes 21 in the nozzle 2, further reducing the gas-liquid two-phase stratification.
  • the through hole in the nozzle 2 can increase the path length of the refrigerant injection, and the distribution pressure difference of the refrigerant can be increased, whereby the flow distribution of the refrigerant is more uniform throughout the length direction of the distribution pipe 1, thereby Improve the heat transfer performance of the heat exchanger.
  • A is the cross-sectional area of the nozzle through hole
  • H is the indenter
  • g is the gravitational acceleration. Is the flow coefficient. Since the nozzle flow coefficient ⁇ ⁇ is 0.82 and the opening flow coefficient on the distribution pipe is 0.62, the flow rate of the nozzle 2 is larger than the flow rate of the opening in the case of the same circulating hydraulic diameter.
  • the refrigerant flows out from the respective openings as it flows through the distribution pipe, the pressure drop of each opening is unequal, and the pressure between the refrigerant inlet and the opening farthest from the refrigerant inlet (the last opening)
  • the difference between the differential and the refrigerant inlet and the opening closest to the refrigerant inlet (the first opening) is large, so the refrigerant flow is not uniform in the length direction of the distribution pipe, and the flow rate from the first opening is required. It's much bigger, and the flow from the last opening is much smaller.
  • the refrigerant distribution device of the embodiment of the present invention since the nozzle 2 having a predetermined length is provided on the distribution pipe 1, the flow path of the refrigerant in each nozzle 2 is increased, the refrigerant The distribution pressure drop is increased compared to the set opening, so the pressure difference between the refrigerant inlet and the first nozzle 2 and the refrigerant inlet and the most The pressure difference between the latter nozzles 2 is closer, so that the distribution of the refrigerant is more evenly hooked in the longitudinal direction of the distribution pipe, as shown in FIG. In Fig.
  • the abscissa s represents the distance between the opening on the conventional distribution pipe and the nozzle 2 according to the embodiment of the present invention to the refrigerant inlet
  • the ordinate m represents the flow rate of the refrigerant from the opening and the nozzle 1.
  • the dispensing pipe 1 is provided with a plurality of nozzles 2, a plurality of tubes along its longitudinal direction (left-right direction in Fig. 1).
  • the mouths 2 are arranged in a line on the dispensing tube 1.
  • the nozzle 2 is a cylinder
  • the through hole 21 is a circular hole
  • the through hole 21 penetrates the outer end surface of the nozzle 2 (for example, the upper end surface in FIG. 1) and the inner end surface. 5 ⁇
  • the length of the through hole 21 is 0. 125-250 times the hydraulic diameter of the through hole 21, for example. It should be noted that if the length of the through hole of the nozzle 1 is too long, the resistance of the refrigerant therein is increased, and if it is too short, the pumping effect is weakened. Therefore, the applicant has obtained a large number of experiments, and controlling the length of the through hole 21 to 0.125-250 times the hydraulic diameter of the through hole 21 can be optimized between reducing the resistance and maintaining the pumping effect.
  • the outer end (upper end in Fig. 1) of the through hole 21 has an enlarged portion 22, thereby facilitating the processing of the through hole 21.
  • the nozzles 2 are equally spaced along the longitudinal direction of the dispensing tube 1, however, the present invention is not limited thereto, and the nozzles 2 may be arranged at unequal intervals.
  • the axial direction of the through hole 21 coincides with the axial direction of the nozzle 2.
  • each nozzle 2 extends into the lumen of the dispensing tube 1 a predetermined distance. Since the nozzle 2 is inserted into the inside of the distribution pipe 1, the refrigerant is disturbed by the nozzle 2 while flowing in the axial direction of the distribution pipe, and the gas and liquid phases are continuously separated and remixed, so that the refrigerant gas and liquid flowing to the rear are both The phase can still be kept even.
  • the inner end of each nozzle 2 is flush with the inner or outer wall of the dispensing tube 1.
  • the through hole 21 penetrates the inner end surface and the outer end surface of the nozzle 2, and the axial direction of the through hole 21 is parallel to the axial direction of the nozzle 2, and the distribution tube 1 is a circular tube, wherein the nozzle
  • the ratio of the ratio H of the length H of the pipe 2 to the hydraulic diameter D of the distribution pipe 1 is in the range of 0. 027-25 and the ratio of the length H of the nozzle 2 to the length L of the distribution pipe 1 is 3. 3 ⁇ in the range of 10-4-0. 125.
  • the nozzle flow can be optimized.
  • H/D when H/D is at 0.027-25 and H/L is at 3. 3 ⁇ 10 - 4 - 0 ⁇ 125, the flow distribution between the respective nozzles 2 of the distribution pipe 1 can be optimized.
  • H 1 - 25 mm
  • d 0.1 - 8 mm
  • D l - 36 mm
  • L 0.2 - 3 m.
  • the flow rate between the respective nozzles 2 of the distribution pipe 1 can be optimized.
  • the dispensing tube 1 is a circular tube, and the through hole 21 in the nozzle 2 is a circular hole.
  • the invention is not limited thereto.
  • the dispensing tube 1 can have a rectangular cross section and the through hole 21 can be a square hole or any other suitable shaped aperture.
  • the nozzle 2 is a cylinder
  • the through hole 21 is a circular hole
  • the through hole 21 penetrates the inner end surface of the nozzle 2 (the lower end surface in FIG. 4) and The outer end surface (the upper end surface in Fig. 4), the axial direction of the through hole 21 is inclined by a predetermined angle ⁇ with respect to the axial direction of the nozzle 2, for example, 0 to 90 degrees, preferably 0 to 60 degrees.
  • the length of the through hole 21 can be lengthened without changing the length of the nozzle 2, thereby increasing the length of the refrigerant flow path, improving the mixing effect of the gas-liquid two-phase refrigerant, and It is possible to change the direction in which the refrigerant path is distributed so that the refrigerant is ejected out of the distribution pipe at a specific angle to enhance the distribution effect.
  • the nozzle 2 is a cylindrical body
  • the through hole 21 penetrates the inner end surface and the outer end surface of the nozzle 2
  • the through hole 21 is a cross-shaped groove.
  • the present invention is not limited thereto, and the through hole 21 may also be a rectangular slot.
  • the inner end of the nozzle 2 projects into the inner cavity of the dispensing tube 1 by a predetermined distance, and the inner end of the nozzle 2 is formed with a bent portion.
  • the tube can be considered
  • the mouth 2 is a bent column.
  • the angle ⁇ between the bend and the nozzle 2 can be in the range of 45-180 degrees.
  • the through hole 21 includes a first through hole portion 212 extending radially along the nozzle 1 and a second through hole portion 211 extending axially along the nozzle 1, second
  • the inner end of the through hole portion 211 communicates with the inner cavity of the distribution pipe 1, the outer end of the second through hole portion 211 is closed, and the first through hole portion 212 communicates the second through hole portion 211 with the outside, in other words, the first through hole
  • the inner end of the portion 212 communicates with the second through hole portion 211, and the outer end of the first through hole portion 212 communicates with the outside.
  • the first through hole portions 212 may be plural, for example, 2-12, and the plurality of first through hole portions 212 are arranged along the circumferential direction of the second through hole portions 21 1 . Since the first through hole portion 212 extends in the radial direction, it is convenient to control the refrigerant to be ejected out of the nozzle in various directions instead of being sprayed radially along the distribution pipe, thereby enhancing the uniformity of distribution of the refrigerant outside the distribution pipe 1, The refrigerant in the space outside the distribution pipe is made more uniform.
  • the through hole 21 includes a plurality of first through hole portions 212 and a second through hole portion 211 extending axially along the nozzle 1, the first through hole portion 212 along the first The circumferential direction of the two through hole portions 211 is arranged.
  • the first through hole portion 212 and the second through hole portion 211 are circular holes, and the first through hole portion 212 is axially offset.
  • the radial direction of the nozzle for example, the tangential direction of the second through hole portion 211, whereby the refrigerant from the first through hole portion 212 is ejected in a direction deviating from the radial direction of the nozzle 1, thereby reinforcing the refrigerant at the injection.
  • the rotation of the time can further enhance the distribution uniformity of the refrigerant outside the distribution pipe, so that the refrigerant distribution in the space outside the gas-liquid two-phase distribution pipe is better.
  • the through hole 21 includes a first through hole portion 212 and a second through hole portion 211 extending axially along the nozzle 2.
  • the first through hole portion 212 and the second through hole portion 211 are respectively rectangular holes.
  • the first through hole portion 212 may be plural, may extend in the radial direction of the nozzle 2, or may be offset from the radial direction of the nozzle 2.
  • a refrigerant distribution device according to an eighth embodiment of the present invention will be described with reference to Figs. 21-23.
  • the nozzles 2 are spirally distributed in the longitudinal direction of the distribution pipe 1, whereby the gas-liquid two-phase refrigerant is spiraled along the longitudinal direction of the distribution pipe 1. It is ejected to achieve the effect of uniformly distributing the gas-liquid two phases of the refrigerant outside the distribution pipe 1.
  • the nozzles 2 are in a row in the longitudinal direction of the dispensing tube 1, however, it is to be understood that the nozzles 2 may be arranged in a plurality of rows in the circumferential direction of the dispensing tube 1, each of which The nozzles 2 in the row are arranged in a spiral or in a straight line.
  • the nozzle 2 is a cylinder, but the invention is not limited thereto, for example, the nozzle 2 may be a prism having a rectangular or other shape cross section.
  • the nozzle 2 can be separately fabricated and mounted to the dispensing tube 1, or alternatively, can be integrally formed with the dispensing tube 1, for example, integrally molded.
  • the nozzle 2 is provided on the distribution pipe 1, the distribution effect can be further improved, the stratification of the gas-liquid two-phase refrigerant can be reduced, and the heat exchange effect can be improved.
  • the heat exchanger according to the embodiment of the present invention includes an inlet header 100, an outlet header 200, a heat exchange tube 300, fins 400, and a refrigerant distribution device.
  • Both ends of the heat exchange tube 2 are connected to the inlet header 100 and the outlet header 200, respectively, to communicate the inlet header 100 and the outlet header 200.
  • the fins 400 are disposed between adjacent heat exchange tubes 300, respectively.
  • the refrigerant distribution device is inserted into The refrigerant distribution device in the inlet header 100 and the refrigerant distribution device is a refrigerant distribution device according to the above embodiment of the present invention. As shown in FIGS. 24 and 25, one end (right end in FIG. 24) of the distribution pipe 1 of the refrigerant distribution device is inserted into the inlet header 100 along the length direction of the inlet header 100, for example, the distribution pipe 1 One end may be closed by a separate end cap or may be closed by the right end wall of the inlet header 100.
  • the other end of the distribution pipe 1 may expose the inlet header 100 and serve as a refrigerant inlet for the heat exchanger.
  • the refrigerant has a good distribution effect and high heat exchange performance.
  • a refrigerant distribution device may also be disposed in the outlet header 200, in which case the refrigerant distribution device functions as a refrigerant collection device.
  • the refrigerant distribution device according to the embodiment of the present invention may be disposed simultaneously in the inlet header 100 and the outlet header 200.
  • the refrigerant distribution device and the heat exchanger according to the embodiment of the present invention have the ability to improve the flow balance, and the pressure relationship between the nozzles can be balanced due to the increase of the flow resistance due to the through hole of the nozzle.
  • the pressure imbalance between the nozzles is greatly reduced, so that the refrigerant flow rate along the length of the distribution pipe is more balanced.
  • the refrigerant distribution device and the heat exchanger according to the embodiment of the present invention have directional control and adjustment capability, and the refrigerant gas-liquid two phases can be sprayed not only along the radial direction of the distribution pipe but also when the nozzle is sprayed out of the nozzle. Spraying along the axial, circumferential or other direction of the distribution tube can greatly improve the spatial refrigerant non-uniformity outside the distribution tube.
  • first embodiment means that Particular features, structures, materials or features described in the examples or examples are included in at least one embodiment or example of the invention.
  • schematic representation of the above terms does not necessarily mean the same embodiment or example.
  • particular features, structures, materials, or characteristics described may be combined in a suitable manner in any one or more embodiments or examples.

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  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
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  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
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Description

制冷剂分配装置和具有它的换热器 技术领域
本发明涉及一种用于换热器的制冷剂分配装置和具有该制冷剂分配装置的换热器。 背景技术
为了保证制冷剂在换热器的换热管内分配均匀， 通常会在换热器的集流管内插入分配 管， 分配管上设有开口， 制冷剂通过开口从分配管进入集流管从而分配到各个换热管内。
传统分配管的不足之处： 在实际使用中， 换热器入口的制冷剂状态为气液两相态， 由 于气相制冷剂与液相制冷剂的密度相差较大， 会产生气液分离现象， 从而影响分配制冷剂 的分配均匀性。 由于气液两相制冷剂直接从分配管表面的开口处流出， 进入集流管中， 气 液两相制冷剂在离开开口时容易产生气液分离， 影响了分配的均匀性。 沿制冷剂流动方向， 各开口之间存在压力不平衡， 从而导致沿分配管长度方向的各开口流量不平衡。。 开口的 数量增加或形式不一， 加工难度增大， 加工面毛刺较多， 清洁较困难。 发明内容
本发明旨在至少解决现有技术中存在的技术问题之一。
为此， 本发明的第一方面的一个目的在于提出一种可以提高制冷剂分配均匀性的制冷 剂分配装置。
本发明的第二方面的一个目的在于提出一种具有根据本发明第一方面的制冷剂分配装 置的换热器， 该换热器换热性能提高。
根据本发明实施例的制冷剂分配装置包括： 分配管， 所述分配管在其长度方向上限定 有第一和第二端， 其中所述分配管上沿所述长度方向设有多个管嘴， 每个管嘴具有预定长 度且形成有通孔， 所述通孔将分配管的内腔与外界连通。
才艮据本发明实施例的制冷剂分配装置， 具有改善流量平衡性的能力， 由于管嘴导致流 动阻力增加， 因而可以平衡各个管嘴之间的压力关系， 使得管嘴之间的压力不平衡大大减 小， 因而沿分配管的长度方向的制冷剂流量更加平衡。
才艮据本发明实施例的制冷剂分配装置， 具有方向控制和调节能力， 制冷剂气液两相在 喷射出管嘴的时候， 可以不仅沿分配管的径向喷射， 还可以沿着分配管轴向、 周向或者其 他方向喷射， 可以使得分配管外的空间制冷剂不均匀性得到大大改善。
另外， 根据本发明上述实施例的制冷剂分配装置还可以具有如下附加的技术特征： 所述多个管嘴在分配管的周向上排列成多排， 其中每一排内的管嘴以螺旋方式排列。 所述通孔为圆孔且贯穿所述管嘴的内端面和外端面， 其中所述通孔的长度为通孔水力 直径的 0. 125-250倍。
所述通孔贯穿所述管嘴的内端面和外端面，且所述通孔的轴向相对于管嘴的轴向倾斜。 所述通孔为矩形槽孔或十字形槽孔。
所述通孔包括沿管嘴径向延伸的第一通孔部和沿管嘴轴向延伸的第二通孔部， 其中所 述第二通孔部的内端与所述分配管的内腔连通， 所述第二通孔部的外端封闭， 所述第一通 孔部将第二通孔部与外界连通。
所述第一通孔部为多个， 所述多个第一通孔部沿第二通孔部的周向布置。
所述通孔包括第一通孔部和沿管嘴轴向延伸的第二通孔部， 其中所述第二通孔部的内 端与所述分配管的内腔连通， 所述第二通孔部的外端封闭， 所述第一通孔部将第二通孔部 与外界连通， 所述第一通孔部的轴向偏离管嘴的径向。
每个管嘴的内端伸入所述分配管的内腔中预定距离。
所述管嘴的内端形成有折弯部。
每个管嘴的内端与所述分配管的内壁或外壁平齐。
所述通孔贯穿所述管嘴的内端面和外端面， 且所述通孔的轴向平行于管嘴的轴向， 所 述分配管为圆形管，其中所述通孔的长度 H与所述分配管的水力直径 D之比 H/D在 0. 027-25 的范围内且所述通孔长度 H与分配管的长度 L之比 H/L在 3. 3 X 10— 4-0. 125的范围内。
所述通孔的横截面积之和与所述分配管的外周表面积之比在 0. 01%-40%的范围内。 根据本发明第二方面的实施例提出一种换热器， 包括： 入口集流管； 出口集流管； 换 热管， 所述换热管的两端分别与入口集流管和出口集流管相连以连通入口集流管和出口集 流管； 翅片， 所述翅片分别设置在相邻的换热管之间； 和制冷剂分配装置， 所述制冷剂分 配装置到所述入口集流管内且所述制冷剂分配装置为才 居本发明第一方面所述的制冷剂分 配装置。
本发明的附加方面和优点将在下面的描述中部分给出， 部分将从下面的描述中变得明 显， 或通过本发明的实践了解到。 附图说明
本发明的上述和 /或附加的方面和优点从结合下面附图对实施例的描述中将变得明显 和容易理解， 其中：
图 1是根据本发明第一实施例的制冷剂分配装置的示意图；
图 2是图 1所示制冷剂分配装置的俯视图；
图 3是图 1所示制冷剂分配装置的横截面示意图； 图 4是根据本发明第二实施例的制冷剂分配装置的局部剖视图；
图 5是图 4所示制冷剂分配装置的俯视图；
图 6是根据本发明第三实施例的制冷剂分配装置的局部剖视图；
图 7是图 6所示制冷剂分配装置的俯视图；
图 8是图 6所示制冷剂分配装置的横截面示意图；
图 9是根据本发明第四实施例的制冷剂分配装置的局部剖视图；
图 10是图 9所示制冷剂分配装置的俯视图；
图 11是图 9所示制冷剂分配装置的横截面示意图；
图 12是根据本发明第五实施例的制冷剂分配装置的局部剖视图；
图 1 3是图 12所示制冷剂分配装置的俯视图；
图 14是图 12所示制冷剂分配装置的横截面示意图；
图 15是根据本发明第六实施例的制冷剂分配装置的示意图；
图 16是图 1 5所示制冷剂分配装置的俯视图；
图 17是图 1 5所示制冷剂分配装置的横截面示意图；
图 18是根据本发明第七实施例的制冷剂分配装置的示意图；
图 19是图 18所示制冷剂分配装置的俯视图；
图 20是图 18所示制冷剂分配装置的横截面示意图；
图 21是根据本发明第八实施例的制冷剂分配装置的示意图；
图 22是图 21所示制冷剂分配装置的俯视图；
图 23是图 21所示制冷剂分配装置的横截面示意图；
图 24是根据本发明实施例的换热器的示意图；
图 25是图 24所示换热器的入口集流管的局部横截面示意图； 和
图 26是才 居本发明实施例的制冷剂分配装置对制冷剂的分配效果与现有分配管对制冷 剂的分配效果的比较曲线图。 具体实施方式
下面详细描述本发明的实施例， 所述实施例的示例在附图中示出， 其中自始至终相同 或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。 下面通过参考附图描 述的实施例是示例性的， 仅用于解释本发明， 而不能理解为对本发明的限制。
在本发明的描述中， 术语 "长度方向"、 "横向"、 "轴向"、 "上"、 "下"、 "前"、 "后"、 "左"、 "右"、 "竖直"、 "水平"、 "顶"、 "底"、 "内"、 "外" 等指示的方位或位置关系为基 于附图所示的方位或位置关系， 仅是为了便于描述本发明而不是要求本发明必须以特定的 方位构造和操作 , 因此不能理解为对本发明的限制。
下面参考附图描述根据本发明实施例的制冷剂分配装置。
如图 1-23所示， 居本发明实施例的制冷剂分配装置包括分配管 1 , 分配管 1在其长 度方向（图 1中的左右方向）上限定有第一端（图 1中的左端）和第二端（图 1中的右端）， 分配管 1上沿其长度方向设有多个管嘴 2 , 每个管嘴 2具有预定长度且形成有通孔 21 , 通 孔 21将分配管 1的内腔与外界连通。 这里， 需要理解的是， 外界是指管嘴 2和分配管 1的 外面， 例如当才 居本发明实施例的制冷剂分配装置安装到换热器的集流管内时， 外界是指 集流管的内腔。
在本发明的一个示例中， 如图 1所示， 分配管 1的第一端敞开， 且第二端封闭， 然而， 需要理解的是， 分配管 1 的第二端可以敞开， 例如可以在安装到换热器的集流管内时由集 流管的端面封闭。 为了便于描述， 下面将分配管 1 的左端作为分配管的入口端， 即分配管 1的左端开口为分配管 1的制冷剂进口。
根据本发明实施例的制冷剂分配装置， 由于在分配管 1上沿其长度方向设有管嘴 2 , 因 此， 在相同的压力下， 在管嘴 2内可以形成泵吸效应， 由此在相同的水力直径下， 管嘴 2 与传统分配管上的开口相比可以提供更大的流量。
此外， 制冷剂流过管嘴 2内的通孔 21的过程中气液两相制冷剂可以重新混合， 进一步 减少了气液两相分层现象。 而且， 管嘴 2 内的通孔可以增加制冷剂喷射的路径长度， 可使 得制冷剂的分配压差增大， 由此在分配管 1 的整个长度方向上， 制冷剂的流量分配更加均 匀， 从而提高换热器的换热性能。
与壁上开设开口的传统分配管相比， 根据本发明实施例的制冷剂分配装置通过在分配 管 1上设置具有预定长度的管嘴 2 , 由于制冷剂的流量 =
Figure imgf000006_0001
, 其中， A为管嘴通孔 的横截面积， H为压头， g为重力加速度， 。为流量系数。 由于管嘴流量系数^ ^为 0. 82 , 而分配管上的开口流量系数为 0. 62 , 因此相同流通水力直径的情况下， 管嘴 2的流量要比 开口的流量大。
此外， 对于传统分配管而言， 制冷剂在流过分配管时从各个开口流出， 各个开口的压 降不均等， 制冷剂进口与距离制冷剂进口最远的开口 （最后一个开口）之间的压差和制冷 剂进口与距离制冷剂进口最近的开口 （第一个开口）之间的压差相差较大， 因此制冷剂流 量在分配管的长度方向上不均匀， 流出第一个开口的流量要大很多， 而流出最后一个开口 的流量要小很多。 相比而言， 根据本发明实施例的制冷剂分配装置， 由于在分配管 1上设 置了具有预定长度的管嘴 2 , 因此， 制冷剂在每个管嘴 2 内的流通路径增长， 制冷剂分配 压降与设置开口相比增大， 因此制冷剂进口与第一个管嘴 2之间的压差和制冷剂进口与最 后一个管嘴 2之间的压差更为接近， 因而制冷剂的分配在分配管长度方向上更加均勾， 如 图 26所示。 在图 26中， 横坐标 s表示传统分配管上的开口和根据本发明实施例的管嘴 2 到制冷剂进口的距离， 纵坐标 m表示制冷剂从开口和管嘴 1流出的流量。
下面参考图 1-3描述才 居本发明第一实施例的制冷剂分配装置。 如图 1-3所示， 才艮据 本发明第一实施例的制冷剂分配装置， 分配管 1上沿其长度方向 （图 1中的左右方向）设 有多个管嘴 2 , 多个管嘴 2在分配管 1上成一条直线排列。
在图 1-3所示的实施例中， 管嘴 2为圆柱体， 通孔 21为圆形孔， 且通孔 21贯穿管嘴 2 的外端面 （例如图 1中的上端面）和内端面 （例如图 1中的下端面）， 其中通孔 21的长度 为通孔 21的水力直径的 0. 125-250倍。 需要说明的是， 如果管嘴 1的通孔长度过长， 则制 冷剂在其内的阻力增加， 过短则会减弱泵吸的效果。 因此， 申请人经过大量的实验得到， 将通孔 21的长度控制在通孔 21的水力直径的 0. 125-250倍可以在降低阻力和维持泵吸效 应之间实现最优化。
如图 1-3所示， 在本发明的一些具体示例中， 通孔 21的外端（图 1中的上端）具有扩 大部 22 , 由此， 便于通孔 21的加工。
如图 1和 1所示， 在本发明的具体示例中， 管嘴 2沿分配管 1长度方向等间距间隔开， 然而， 本发明并不限于此， 管嘴 2也可以不等间距地排列。
如图 3所示， 在本发明的一个示例中， 通孔 21的轴向与管嘴 2的轴向一致。
在本发明的另一些示例中， 每个管嘴 2 的内端 （即管嘴靠近分配管的一端）伸入分配 管 1的内腔中预定距离。 由于管嘴 2插入到分配管 1的内部， 制冷剂在沿分配管的轴向流 动时受到管嘴 2的扰动， 气液相不断发生分离和再混合， 使得流到后面的制冷剂气液两相 仍能保持均匀。 可选地， 每个管嘴 2的内端与分配管 1的内壁或外壁平齐。
在本发明的一些实施例中， 通孔 21贯穿管嘴 2的内端面和外端面， 且通孔 21的轴向 平行于管嘴 2的轴向， 分配管 1为圆形管， 其中管嘴 2的长度 H与分配管 1的水力直径 D 之比 H/D在 0. 027-25的范围内且管嘴 2的长度 H与分配管 1的长度 L之比 H/L在 3. 3 χ 10— 4-0. 125的范围内。
根据本发明的实施例， 如果不考虑局部压降， 根据分配管内沿程阻力的公式，
ΔΡ =λ (1 /d) pu2/2
单个管嘴的阻力
ΔΡ =λ1 (H/d) puV2
而分配管内的沿程阻力 ΔΡ f =X2 (L/D) pu2/2
当 ΔΡ管嘴大于 ΔΡ管时， 即可实现管嘴流量的优化。
据此， 当 H/D在 0. 027-25和 H/L在 3. 3 χ 10— 4- 0· 125时, 分配管 1的各个管嘴 2之间 的流量分配能得到优化。 例如， 在本发明的一个具体示例中， H=l-25毫米， d=0. 1-8毫米， D=l-36毫米， L=0. 2-3米。
同样， 基于上述分析， 在通孔 21 的横截面积之和与分配管 1 的外周表面积之比在 0. 01%-40%的范围内时， 分配管 1的各个管嘴 2之间的流量分配能得到优化。
在图 1-3所示的实施例中， 分配管 1为圆形管， 管嘴 2内的通孔 21为圆形孔。 然而， 本发明并不限于此。 例如， 在本发明的另一些实施例中， 分配管 1可以具有矩形截面， 通 孔 21可以为方形孔或其他任何合适形状的孔。
下面参考图 4和图 5描述才 居本发明第二实施例的制冷剂分配装置。 在图 4和图 5所 示的第二实施例中， 管嘴 2为圆柱体， 通孔 21为圆形孔， 且通孔 21贯穿管嘴 2的内端面 (图 4中的下端面）和外端面 （图 4中的上端面）， 通孔 21的轴向相对于管嘴 2的轴向倾 斜预定角度 α , 例如 0-90度， 优选 0-60度。 通过将通孔 21设置成倾斜的， 可以在不改变 管嘴 2长度的情况下， 延长通孔 21的长度， 从而增加制冷剂流动通路的长度， 提高气液两 相制冷剂的混合效果， 并且能够改变分配制冷剂路径的方向， 使得制冷剂沿特定角度喷射 出分配管， 加强分配效果。
下面参考图 6-8描述才 居本发明第三实施例的制冷剂分配装置。 在图 6-8所示的第三 实施例中， 管嘴 2为圆柱体， 通孔 21贯穿管嘴 2的内端面和外端面， 通孔 21为十字形槽 孔。 然而， 本发明并不限于此， 通孔 21也可以为矩形槽孔。 通过将通孔 21形成为非圆形 的狭槽， 可以进一步提高泵吸效应和喷射效果， 消除气液分层现象。
下面参考图 9-11描述才 居本发明第四实施例的制冷剂分配装置。 在图 9-11所示的第 四实施例中， 管嘴 2的内端伸入分配管 1的内腔中预定距离， 且管嘴 2的内端形成有折弯 部， 换言之， 可以认为管嘴 2为折弯的柱状。 折弯部与管嘴 2之间的夹角 β可以在 45-180 度的范围内。 通过在管嘴 2的内端形成折弯部， 可以对气液制冷剂起到导引作用， 并且对 制冷剂在分配管 1内的流动的搅动作用进一步增强。
下面参考图 12-1 3描述才 居本发明第五实施例的制冷剂分配装置。在图 9-11所示的第 五实施例中，通孔 21包括沿管嘴 1径向延伸的第一通孔部 212和沿管嘴 1轴向延伸的第二 通孔部 211 , 第二通孔部 211的内端与分配管 1的内腔连通， 第二通孔部 211的外端封闭， 第一通孔部 212将第二通孔部 211与外界连通， 换言之， 第一通孔部 212的内端与第二通 孔部 211连通， 第一通孔部 212的外端与外界连通。 在本发明的一个具体示例中， 第一通 孔部 212可以为多个， 例如 2-12个， 多个第一通孔部 212沿第二通孔部 21 1的周向布置。 由于第一通孔部 212沿着径向延伸， 因此可以方便控制制冷剂沿各个方向喷射出管嘴， 而 非沿分配管径向喷射， 增强了制冷剂在分配管 1外的分配均匀性， 使得分配管外的空间内 制冷剂更加均匀。
下面参考图 15-17描述才 居本发明第六实施例的制冷剂分配装置。 在图 15-17所示的 第六实施例中， 通孔 21包括多个第一通孔部 212和沿管嘴 1轴向延伸的第二通孔部 211 , 第一通孔部 212沿第二通孔部 211的周向布置， 在图 15-17所示的实施例中， 第一通孔部 212和第二通孔部 211为圆形孔， 第一通孔部 212的轴向偏离管嘴 2的径向， 例如第二通 孔部 211的切线方向， 由此， 从第一通孔部 212出来的制冷剂沿偏离管嘴 1径向的方向喷 出， 从而加强制冷剂在喷射时的旋转， 更能增强制冷剂在分配管外的分配均匀性， 使得气 液两相分配管外的空间内制冷剂分布更佳。
下面参考图 18-20描述才 居本发明第七实施例的制冷剂分配装置。 在图 18-20所示的 第七实施例中， 通孔 21包括第一通孔部 212和沿管嘴 2轴向延伸的第二通孔部 211。 其中 第一通孔部 212和第二通孔部 211分别为矩形孔。 第一通孔部 212可以为多个， 可以沿管 嘴 2的径向延伸， 也可以偏离管嘴 2的径向。
下面参考图 21-23描述才 居本发明第八实施例的制冷剂分配装置。 在图 21-23所示的 第八实施例中， 管嘴 2在分配管 1的长度方向上成螺旋状分布， 由此， 气液两相制冷剂会 沿分配管 1的长度方向以螺旋状喷射出， 从而达到制冷剂的气液两相在分配管 1外面均匀 分布的效果。
在本发明的上述实施例中， 管嘴 2在分配管 1的长度方向上为一排， 然而， 需要理解 的是， 管嘴 2在分配管 1的周向上可以排列成多排， 其中每一排内的管嘴 2以螺旋方式排 列或直线排列。
在本发明的上述实施例中， 管嘴 2为圆柱体， 然而本发明并不限于此， 例如管嘴 2可 以为具有矩形或其他形状横截面的棱柱体
才艮据本发明的一些实施例， 管嘴 2可以单独制成后安装到分配管 1上， 可选地， 可以 与分配管 1一体制成， 例如一体铸成。
根据本发明实施例的制冷剂分配装置， 由于在分配管 1上设置了管嘴 2 , 因此能够进一 步提高分配效果， 减少气液两相制冷剂分层， 提高换热效果。
下面参考 24和 25描述 据本发明实施例的换热器。 如图 24和 25所示， 居本发明 实施例的换热器包括入口集流管 100 , 出口集流管 200 , 换热管 300 , 翅片 400 , 制冷剂分 配装置。
换热管 2的两端分别与入口集流管 100和出口集流管 200相连以连通入口集流管 100 和出口集流管 200。 翅片 400分别设置在相邻的换热管 300之间。 制冷剂分配装置插入到 入口集流管 100 内且所述制冷剂分配装置为根据本发明上述实施例描述的制冷剂分配装 置。 如图 24和 25所示， 制冷剂分配装置的分配管 1的一端 （图 24中的右端） 沿入口集 流管 100的长度方向插入到入口集流管 100内， 例如， 所述分配管 1的一端可以用单独的 端盖封闭，也可以通过入口集流管 100的右端壁封闭。分配管 1的另一端（图 24中的左端） 可以露出入口集流管 100且作为换热器的制冷剂入口。 居本发明实施例的换热器， 制冷 剂的分配效果好， 换热性能高。
需要理解的是， 根据本发明的实施例， 在出口集流管 200 内也可以设置根据本发明实 施例的制冷剂分配装置， 在此情况下， 制冷剂分配装置用作制冷剂收集装置。 可选地， 根 据本发明实施例的制冷剂分配装置可以同时设置在入口集流管 100和出口集流管 200内。
综上所述， 根据本发明实施例的制冷剂分配装置和换热器， 具有改善流量平衡性的能 力， 由于管嘴的通孔导致流动阻力增加， 因而可以平衡各个管嘴之间的压力关系， 使得管 嘴之间的压力不平衡大大减小， 因而沿分配管的长度方向的制冷剂流量更加平衡。
才艮据本发明实施例的制冷剂分配装置和换热器， 具有方向控制和调节能力， 制冷剂气 液两相在喷射出管嘴的时候， 可以不仅沿分配管的径向喷射， 还可以沿着分配管轴向、 周 向或者其他方向喷射， 可以使得分配管外的空间制冷剂不均匀性得到大大改善。
在本说明书的描述中， 参考术语 "第一实施例"、 "一些实施例"、 "第二实施例"、 "示 例"、 "具体示例"、 或 "一些示例" 等的描述意指结合该实施例或示例描述的具体特征、 结 构、 材料或者特点包含于本发明的至少一个实施例或示例中。 在本说明书中， 对上述术语 的示意性表述不一定指的是相同的实施例或示例。 而且， 描述的具体特征、 结构、 材料或 者特点可以在任何的一个或多个实施例或示例中以合适的方式结合。
尽管已经示出和描述了本发明的实施例， 本领域的普通技术人员可以理解： 在不脱离 本发明的原理和宗旨的情况下可以对这些实施例进行多种变化、 修改、 替换和变型， 本发 明的范围由权利要求及其等同物限定。

Claims

权 利 要 求 书
1、一种制冷剂分配装置， 其特征在于， 包括： 分配管， 所述分配管在其长度方向上限 定有第一和第二端， 其中所述分配管上沿所述长度方向设有多个管嘴， 每个管嘴具有预定 长度且形成有通孔， 所述通孔将分配管的内腔与外界连通。
2、 根据权利要求 1所述的制冷剂分配装置， 其特征在于， 所述多个管嘴在分配管的周 向上排列成多排， 其中每一排内的管嘴以螺旋方式排列。
3、 根据权利要求 1所述的制冷剂分配装置， 其特征在于， 所述通孔为圆孔且贯穿所述 管嘴的内端面和外端面， 其中所述通孔的长度为通孔水力直径的 0. 125-250倍。
4、 根据权利要求 1所述的制冷剂分配装置， 其特征在于， 所述通孔贯穿所述管嘴的内 端面和外端面， 且所述通孔的轴向相对于管嘴的轴向倾斜。
5、 根据权利要求 1所述的制冷剂分配装置， 其特征在于， 所述通孔为矩形槽孔或十字 形槽孔。
6、 根据权利要求 1所述的制冷剂分配装置， 其特征在于， 所述通孔包括沿管嘴径向延 伸的第一通孔部和沿管嘴轴向延伸的第二通孔部， 其中所述第二通孔部的内端与所述分配 管的内腔连通， 所述第二通孔部的外端封闭， 所述第一通孔部将第二通孔部与外界连通。
7、 根据权利要求 6所述的制冷剂分配装置， 其特征在于， 所述第一通孔部为多个， 所 述多个第一通孔部沿第二通孔部的周向布置。
8、 根据权利要求 1所述的制冷剂分配装置， 其特征在于， 所述通孔包括第一通孔部和 沿管嘴轴向延伸的第二通孔部， 其中所述第二通孔部的内端与所述分配管的内腔连通， 所 述第二通孔部的外端封闭， 所述第一通孔部将第二通孔部与外界连通， 所述第一通孔部的 轴向偏离管嘴的径向。
9、 根据权利要求 1-8中任一项所述的制冷剂分配装置， 其特征在于， 每个管嘴的内端 伸入所述分配管的内腔中预定距离。
10、 根据权利要求 9所述的制冷剂分配装置， 其特征在于， 所述管嘴的内端形成有折 弯部。
11、 根据权利要求 1-8 中任一项所述的制冷剂分配装置， 其特征在于， 每个管嘴的内 端与所述分配管的内壁或外壁平齐。
12、 根据权利要求 1 所述的制冷剂分配装置， 其特征在于， 所述通孔贯穿所述管嘴的 内端面和外端面， 且所述通孔的轴向平行于管嘴的轴向， 所述分配管为圆形管， 其中所述 通孔的长度 H与所述分配管的水力直径 D之比 H/D在 0. 027-25的范围内且所述通孔长度 H 与分配管的长度 L之比 H/L在 3. 3 X 10— 4- 0· 125的范围内。
1 3、 根据权利要求 1 所述的制冷剂分配装置， 其特征在于， 所述通孔的横截面积之和 与所述分配管的外周表面积之比在 0. 01%-40%的范围内。
14、 一种换热器， 其特征在于， 包括：
入口集流管；
出口集流管；
换热管， 所述换热管的两端分别与入口集流管和出口集流管相连以连通入口集流管和 出口集流管；
翅片， 所述翅片分别设置在相邻的换热管之间； 和
制冷剂分配装置， 所述制冷剂分配装置到所述入口集流管内且所述制冷剂分配装置为 根据权利要求 1-1 3中任一项所述的制冷剂分配装置。
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103868398A (zh) * 2014-02-26 2014-06-18 美的集团股份有限公司 集流管及具有该集流管的平行流换热器
JP2016525667A (ja) * 2013-07-30 2016-08-25 サンホワ（ハンチョウ） マイクロ チャンネル ヒート イクスチェンジャー カンパニー リミテッド ヘッダー組立体及び該ヘッダー組立体を備えた熱交換器

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103868287B (zh) * 2012-12-18 2016-02-03 珠海格力电器股份有限公司 制冷剂分配器及其所应用的换热器
CN104344607B (zh) * 2013-08-08 2018-07-06 浙江盾安热工科技有限公司 一种换热器
CN103604254B (zh) * 2013-11-12 2016-07-06 清华大学 一种内置气液两相流分流结构
US9915456B2 (en) 2015-06-03 2018-03-13 Mitsubishi Electric Research Laboratories, Inc. System and method for controlling vapor compression systems
KR102151217B1 (ko) * 2015-12-07 2020-09-02 에스트라오토모티브시스템 주식회사 공기조화기용 증발기의 냉매 분배관
JP6850058B2 (ja) * 2016-07-12 2021-03-31 マーレベーアサーマルシステムズジャパン株式会社 コンデンサ
US11156412B2 (en) * 2016-09-12 2021-10-26 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus
EP3548824B1 (fr) * 2016-11-30 2023-03-29 Valeo Systemes Thermiques Dispositif d'homogénéisation de la distribution d'un fluide réfrigérant à l'intérieur de tubes d'un échangeur de chaleur constitutif d'un circuit de fluide réfrigérant
CN110940220B (zh) * 2018-09-25 2022-03-01 丹佛斯有限公司 用于换热器的分配管组件和具有该分配管组件的集流管组件和换热器
DE102019207799A1 (de) * 2019-05-28 2020-12-03 Mahle International Gmbh Tauchrohr zur Kältemittelverteilung in einem Chiller
EP3757498A1 (en) * 2019-06-26 2020-12-30 Valeo Autosystemy SP. Z.O.O. Heat exchanger

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004278935A (ja) * 2003-03-17 2004-10-07 Calsonic Kansei Corp 蒸発器
WO2006039148A2 (en) * 2004-10-01 2006-04-13 Advanced Heat Transfer, Llc Refrigerant distribution device and method
WO2006039086A2 (en) * 2004-10-01 2006-04-13 Advanced Heat Transfer, Llc Refrigerant distribution device and method
CN1920369A (zh) * 2006-09-20 2007-02-28 浙江大学 一种气体分布器
WO2008060270A1 (en) * 2006-11-13 2008-05-22 Carrier Corporation Minichannel heat exchanger header insert for distribution
CN101660870A (zh) * 2009-09-16 2010-03-03 三花丹佛斯（杭州）微通道换热器有限公司 具有改进制冷剂分配性能的换热器
CN101839590A (zh) * 2010-02-22 2010-09-22 三花丹佛斯（杭州）微通道换热器有限公司 一种微通道换热器
CN201757545U (zh) * 2010-06-28 2011-03-09 赵敏 一种换热器
CN102072684A (zh) * 2011-01-06 2011-05-25 三花丹佛斯（杭州）微通道换热器有限公司 制冷剂分配装置和具有它的换热器

Family Cites Families (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS48114352U (zh) * 1972-04-03 1973-12-27
JPS5062742U (zh) * 1973-10-03 1975-06-07
US4058262A (en) * 1976-02-13 1977-11-15 Bete Fog Nozzle Inc. Fluid spray for generating rectangular coverage
US4265840A (en) * 1978-09-25 1981-05-05 Baehler Paul Vapor distributor pipe for air humidifier
GB2046421B (en) * 1979-02-20 1983-05-05 Linde Ag Spraying system for delivering a liquid cryogenic coolant into an insulated freezing chamber
US4568022A (en) * 1980-04-04 1986-02-04 Baltimore Aircoil Company, Inc. Spray nozzle
US4384873A (en) * 1982-02-10 1983-05-24 Herrmidifier Company, Inc. Central steam humidifier
CN2034087U (zh) * 1988-06-24 1989-03-15 国家机械工业委员会西安重型机械研究所 带有分导雾化片的喷嘴
US5291943A (en) * 1992-12-29 1994-03-08 The Regents Of The University Of California Heat transfer enhancement using tangential injection
JPH073737U (ja) * 1993-06-24 1995-01-20 株式会社平田精機 散水装置
JPH08189725A (ja) * 1995-01-05 1996-07-23 Nippondenso Co Ltd 冷媒蒸発器
JP3597268B2 (ja) * 1995-09-27 2004-12-02 昭和電工株式会社 中空成形内部冷却用吹込ピン
US5730366A (en) * 1996-04-04 1998-03-24 Dewitt; Robert E. Oscillating, transverse-axis water sprinkler with see-saw spray arm and twist-positionable nozzles
EP0878221B1 (de) * 1997-05-16 2003-11-05 Sulzer Chemtech AG Verteilvorrichtung für eine Kolonne
EP1340954B1 (de) * 2002-02-27 2005-12-07 Axima Refrigeration GmbH Verteilsystem
US6814136B2 (en) * 2002-08-06 2004-11-09 Visteon Global Technologies, Inc. Perforated tube flow distributor
EP1548380A3 (en) * 2003-12-22 2006-10-04 Hussmann Corporation Flat-tube evaporator with micro-distributor
US7744068B2 (en) * 2006-09-13 2010-06-29 Dristeem Corporation Insulation for a steam carrying apparatus and method of attachment thereof
RU2351403C1 (ru) * 2007-11-21 2009-04-10 Государственное научное учреждение Поволжский научно-исследовательский институт эколого-мелиоративных технологий Российской академии сельскохозяйственных наук Вихревой дождевальный насадок-активатор
CN101932893B (zh) * 2008-01-11 2013-07-03 江森自控科技公司 热交换器
US20090229805A1 (en) * 2008-03-13 2009-09-17 Delphi Technologies, Inc. Manifold design having an improved collector conduit and method of making same
CN201443932U (zh) * 2008-11-15 2010-04-28 倪绍科 可拆洗喷淋式地源热泵蒸发器
CN101782338A (zh) * 2009-01-21 2010-07-21 三花丹佛斯（杭州）微通道换热器有限公司 热交换器
CN101788235B (zh) * 2009-03-25 2013-07-24 三花控股集团有限公司 热交换器
CN101691981B (zh) * 2009-07-23 2011-12-07 三花丹佛斯（杭州）微通道换热器有限公司 具有改进的制冷剂流体分配均匀性的多通道换热器
US8920956B2 (en) * 2010-08-23 2014-12-30 Lg Chem, Ltd. Battery system and manifold assembly having a manifold member and a connecting fitting

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004278935A (ja) * 2003-03-17 2004-10-07 Calsonic Kansei Corp 蒸発器
WO2006039148A2 (en) * 2004-10-01 2006-04-13 Advanced Heat Transfer, Llc Refrigerant distribution device and method
WO2006039086A2 (en) * 2004-10-01 2006-04-13 Advanced Heat Transfer, Llc Refrigerant distribution device and method
CN1920369A (zh) * 2006-09-20 2007-02-28 浙江大学 一种气体分布器
WO2008060270A1 (en) * 2006-11-13 2008-05-22 Carrier Corporation Minichannel heat exchanger header insert for distribution
CN101660870A (zh) * 2009-09-16 2010-03-03 三花丹佛斯（杭州）微通道换热器有限公司 具有改进制冷剂分配性能的换热器
CN101839590A (zh) * 2010-02-22 2010-09-22 三花丹佛斯（杭州）微通道换热器有限公司 一种微通道换热器
CN201757545U (zh) * 2010-06-28 2011-03-09 赵敏 一种换热器
CN102072684A (zh) * 2011-01-06 2011-05-25 三花丹佛斯（杭州）微通道换热器有限公司 制冷剂分配装置和具有它的换热器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2650635A4 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016525667A (ja) * 2013-07-30 2016-08-25 サンホワ（ハンチョウ） マイクロ チャンネル ヒート イクスチェンジャー カンパニー リミテッド ヘッダー組立体及び該ヘッダー組立体を備えた熱交換器
US9885527B2 (en) 2013-07-30 2018-02-06 Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. Manifold assembly and heat exchanger having manifold assembly
CN103868398A (zh) * 2014-02-26 2014-06-18 美的集团股份有限公司 集流管及具有该集流管的平行流换热器
CN103868398B (zh) * 2014-02-26 2016-08-31 美的集团股份有限公司 集流管及具有该集流管的平行流换热器

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