WO2019210690A1 - 换热管、换热器及热泵机组 - Google Patents

换热管、换热器及热泵机组 Download PDF

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Publication number
WO2019210690A1
WO2019210690A1 PCT/CN2018/121202 CN2018121202W WO2019210690A1 WO 2019210690 A1 WO2019210690 A1 WO 2019210690A1 CN 2018121202 W CN2018121202 W CN 2018121202W WO 2019210690 A1 WO2019210690 A1 WO 2019210690A1
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WIPO (PCT)
Prior art keywords
heat exchange
fin
exchange tube
tube according
fins
Prior art date
Application number
PCT/CN2018/121202
Other languages
English (en)
French (fr)
Inventor
刘华
张治平
岳清学
胡东兵
王春连
张营
杨旭峰
Original Assignee
珠海格力电器股份有限公司
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
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Application filed by 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Priority to EP18917408.9A priority Critical patent/EP3736521B1/en
Priority to RU2020131269A priority patent/RU2760467C1/ru
Publication of WO2019210690A1 publication Critical patent/WO2019210690A1/zh

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    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with 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
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • 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
    • F28F1/006—Tubular elements; Assemblies of tubular elements with variable shape, e.g. with modified tube ends, with different geometrical features
    • 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
    • F28F1/24—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 and extending transversely
    • F28F1/26—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 and extending transversely the means being integral with the 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
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/424—Means comprising outside portions integral with inside portions
    • F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/007—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • the present disclosure relates to the field of air conditioning, and more particularly to a heat exchange tube, a heat exchanger, and a heat pump unit.
  • the heat exchanger for the full-liquid heat pump unit is divided into a full-liquid evaporator and a full-liquid condenser due to its different functions and working principles, and is a heat exchanger of two different structural forms.
  • the heat transfer tubes which are the core components of a flooded heat exchanger, are also classified into a full liquid evaporation tube and a full liquid condensation tube.
  • the heat exchanger structure needs to be redesigned and adjusted to obtain a heat exchanger structure type that can satisfy both evaporation and condensation.
  • the development of heat exchange tubes for evaporative condensation in heat exchangers has become a bottleneck in unit development.
  • One of the objects of some embodiments of the present disclosure is to propose a heat exchange tube, heat exchanger, and heat pump unit that combines evaporation and condensation.
  • a heat exchange tube includes a tube body and fins disposed on an outer surface of the tube; the fins include: a wing root portion disposed on an outer surface of the tube body; a portion provided at a top of the wing root portion and extending to both sides of the wing root portion; and a wing top portion provided at a top portion of the lateral wing portion, configured in a zigzag shape, and the concave portion in the zigzag shape Extending to the transverse fins.
  • the fins are spirally or parallelly disposed on an outer surface of the tubular body, and channels are formed between the fins, and a gap is formed between adjacent ones of the transverse fins in the passage.
  • the fins are spirally or parallelly disposed on an outer surface of the tubular body, and the transverse fins divide the channel formed between the fins into an outer cavity and an inner cavity, the inner cavity being opposite The outer cavity is adjacent to an outer surface of the tubular body.
  • a first groove is provided on a wall surface of the inner cavity.
  • the first groove is provided on an outer surface of the tubular body.
  • the first groove is a "work" shape, a "ten” shape, an "X” shape, a “U” shape, a triangle, or a polygon of three or more sides.
  • the transverse fins are configured to be curvilinear, or the surface of the transverse fins is configured to be curvilinear.
  • the transverse fin portion is provided with a plurality of slits, at least one of which is connected to a recess of the serrated shape.
  • each of the slits is correspondingly coupled to a recess of the serration.
  • At least the lateral fins on one side of the wing root are inclined toward the outer surface of the tubular body.
  • the transverse fins on either side of the root of the wing are symmetrically inclined toward the outer surface of the tubular body.
  • the first cross-section of the serrated protrusion is trapezoidal, triangular or rectangular, the first cross-section being substantially perpendicular to the axis of the tubular body.
  • the second cross-section of the serrated protrusion is rectangular, parallelogram or trapezoidal, the second section being substantially parallel to the axis of the tubular body.
  • the serrated recess is trapezoidal, triangular or rectangular.
  • At least one side of the fin top is provided with at least one of a spike and a second groove.
  • the number of the serrated protrusions is 40 to 95 on a section of the fin along a circumference of the tube.
  • the inner surface of the tubular body is provided with a thread, and the tangent of the thread is at an angle of 15 to 65 with respect to the center line of the tubular body.
  • Some embodiments of the present disclosure provide a heat exchanger that includes the heat exchange tubes described above.
  • Some embodiments of the present disclosure provide a heat pump assembly that includes the heat exchanger described above.
  • the heat pump unit is a flooded heat pump unit.
  • a heat exchange tube includes a tube body and fins disposed on an outer surface of the tube body; the fin includes a wing root portion, a lateral wing portion, and a fin top portion, and the top of the fin is disposed at the top of the lateral wing portion Constructed in a zigzag shape, and the concave portion in the zigzag shape extends to the lateral fin portion, which facilitates the expansion of the heat exchange area at the top of the fin, diluting the liquid film, and the serrated wing top facilitates the flow of the refrigerant to improve the condensation performance; the transverse fin portion is finned The two sides extend to form an underlying channel and an upper channel which facilitate evaporation and condensation, so that the heat exchange tube balances evaporation performance and condensation performance.
  • FIG. 1 is an overall schematic view showing a heat exchange tube in accordance with some embodiments of the present disclosure
  • FIG. 2 is a partial schematic view showing a heat exchange tube in accordance with some embodiments of the present disclosure
  • FIG. 3 is a cross-sectional schematic view showing a heat exchange tube in accordance with some embodiments of the present disclosure
  • FIG. 4 is a partial enlarged schematic view showing a heat exchange tube in accordance with some embodiments of the present disclosure
  • FIG. 5 is a partial enlarged schematic view showing fins of a heat exchange tube in accordance with some embodiments of the present disclosure
  • FIG. 6 is a partial side elevational view showing a heat exchange tube in accordance with some embodiments of the present disclosure
  • FIG. 7 is a partial enlarged schematic view showing fins of a heat exchange tube in accordance with some embodiments of the present disclosure.
  • the heat exchange tube comprises a tubular body 10 comprising an unprocessed smooth section 11, a fully finned finned section 13 along the circumference, and a smooth section 11 and a finned section Transition section 12 between 13.
  • the smooth section 11 is used for expansion and sealing between the shell tube and the heat exchange tubes.
  • the heat exchange tube When the heat exchange tube is operated in the unit, it is kept in a vibrating state for a long time, and the transition portion 12 is used to increase the strength of the heat exchange tube.
  • the outer diameter of the transition section 12 is smaller than the outer diameter of the smooth section 11.
  • the heat exchange tube includes a tube body 10 and fins 20 disposed on an outer surface of the tube body 10.
  • the fins 20 are provided in the finned section 13 of the tubular body 10.
  • the fins 20 are helical fins that are helically disposed in the tubular body 10 along the axial direction of the tubular body 10.
  • the fins 20 include a plurality of annular fins disposed along the circumference of the tubular body 10, and each annular fin is spaced along the axial direction of the tubular body 10. Further, each of the annular fins is disposed in parallel.
  • the fins 20 include a plurality of linear fins having a longitudinal direction that coincides with the axial direction of the tubular body 10, and the linear fins are spaced apart along the circumference of the tubular body 10. Further, each of the linear fins is disposed in parallel.
  • the fin 20 includes a wing root portion 23, a transverse wing portion 21, and a fin top portion 22.
  • the wing roots 23 are provided on the outer surface of the tubular body 10.
  • the transverse fins 21 are provided at the top of the wing roots 23 and extend to both sides of the wing roots 23. Below the transverse fin portion 21, a space for facilitating the evaporation performance is formed with the wing root portion 23 and the outer surface of the tubular body 10.
  • the fin top 22 is disposed at the top of the lateral fin portion 21, is configured in a zigzag shape, and the concave portion of the serrated portion of the fin top portion 22 extends to the lateral fin portion 21 for expanding the fin top portion 22
  • the hot area, the thin liquid film, and the serrated wing top 22 facilitate the flow of the refrigerant to improve the condensation performance.
  • the fin top 22 has a thickness that is less than the thickness of the wing root 22, facilitating the formation of sharp edges at the fin top 22, piercing the liquid-carrying gaseous refrigerant.
  • the top of the fin 20 is formed into a fin top 22 by extrusion, the thickness of the fin top 22 being thin relative to the thickness of the wing root 23, and the transverse fin portion 21 being finned relative to the wing root 23 and the fin top 22 The two sides of the 20 extend.
  • the fin top 22 is configured in a zigzag shape, and the concave portion in the zigzag shape extends to the lateral fin portion 21, and the lateral fin portion 21 extends to both sides of the fin 20.
  • the structure combines evaporation performance and condensation performance, alleviating the performance degradation problem when a conventional condenser tube is used as an evaporation tube; and alleviating the performance degradation problem when a conventional evaporation tube is used as a condensation tube.
  • the fins 20 are spirally or parallelly disposed on the outer surface of the tube body 10, the channels of the spiral fins form a channel, or the adjacent fins of the plurality of fins form a channel. There is a gap 26 between adjacent transverse fins 21 in the channel.
  • one of the lateral fin portions 21 is higher in the fin height direction than the adjacent lateral fin portion 21.
  • the end (overlapping portion) of one of the lateral fin portions 21 is higher in the fin height direction than the end (overlapping portion portion) of the lateral fin portion 21 adjacent thereto.
  • gaps 26 between adjacent transverse fins 21 in the channel opening up the upper and lower channels between the fins and the fins, facilitating the flow of liquid refrigerant, enhancing the condensation effect; and evaporating the refrigerant.
  • it is conducive to the replenishment of refrigerant and the discharge of gaseous refrigerant, which enhances the evaporation function; both evaporation and condensation are not attenuated.
  • the fins 20 are helically or parallelly disposed on the outer surface of the tubular body 10, and the transverse fins 21 divide the passage formed between the fins 20 into an outer cavity 24 and an inner cavity 25, the inner cavity 25 being opposed to the outer cavity 24 is adjacent to the outer surface of the tubular body 10.
  • the transverse fins 21 divide the channel formed between the fins 20 into an outer cavity 24 and an inner cavity 25, with a gap 26 between adjacent transverse fins 21 in the channel, the gap 26 facilitating the lower layer evaporation
  • the inner cavity 25 is surrounded by the lateral fin portion 21, the wing root portion 23 and the outer surface of the tubular body 10, and mainly forms a small cavity for evaporation, and the principle adopted is mainly the principle of nucleate boiling.
  • the outer cavity 25 is surrounded by the transverse fin portion 21 and the fin top portion 22, mainly to increase the heat exchange area and to dilute the liquid film to facilitate condensation. Therefore, it is advantageous to achieve neither evaporation nor condensation.
  • the first cavity 251 is disposed on the wall surface of the inner cavity 25, and the surface of the inner cavity 25 is roughened by providing the first groove 251, which is favorable for forming a vaporization core required for evaporation, and enhancing evaporation heat transfer. .
  • the first groove 251 may be provided on an outer surface of the tube body 10. Since the coolant is introduced into the pipe body 10 for heat exchange with the refrigerant outside the pipe body 10, the first groove 251 is disposed on the outer surface of the pipe body 10, which facilitates formation of a vaporization core on the outer surface of the pipe body 10, strengthening Evaporation heat transfer; in addition, the heat exchange area can be increased on the outer surface of the original smooth pipe body 10. Further, the outer surface of the pipe body 10 is provided with a plurality of first grooves 251 along the passage direction between the fins 20.
  • the smoothing roller is used to perform a rolling flattening process on the outer surface of the tubular body 10 such that a multi-pit surface structure can be formed on the outer surface of the tubular body 10 to provide a vaporized core required for evaporation. Enhanced evaporation heat transfer.
  • the first groove 251 can be provided on the surface of the wing root 23 to facilitate formation of a vaporization core. Further, the first groove 251 may be disposed along the height direction of the wing root portion 23 to facilitate the flow of the refrigerant along the first groove 251.
  • the first groove 251 has a "work” shape, a "ten” shape, an "X” shape, a "U” shape, a circle, a triangle, a quadrangle, a polygon larger than four sides, or other irregularities. Or the shape of the rule, etc.
  • a plurality of first grooves 251 are disposed in the inner cavity 25.
  • the uneven structure facilitates increasing the roughness of the inner cavity 25, facilitating the formation of a vaporization core, and enhancing the evaporation function.
  • the lateral fin portion 21 is configured to be curved, or the surface of the lateral fin portion 21 is configured to be curved.
  • the body or surface of the transverse fin portion 21 is configured to be curved to facilitate an increase in the heat exchange area, to attenuate the liquid film, and to facilitate the flow of the refrigerant.
  • the transverse fin portion 21 is provided with a slit 211 that facilitates the passage of fluid to facilitate replenishment of the refrigerant and escape of vaporized bubbles.
  • the transverse fin portion 21 is provided with a plurality of slits 211, each of which is correspondingly connected to a serrated recess of the fin top portion 22.
  • the provision of the slit 211 facilitates the flow of the refrigerant, and the slit 211 is connected to the recess of the fin top 22 to facilitate the flow of the refrigerant to the inner cavity 25.
  • the slit 211 may be elongated and extend in the extending direction of the lateral fin portion 21.
  • the transverse fin portion 21 is provided with a plurality of circular, triangular, square, or polygonal shapes of more than four sides, or other regular or irregular through holes to facilitate the flow of the refrigerant to the inner cavity 25 or the gaseous refrigerant. Discharge.
  • At least the lateral fin portion 21 on the side of the wing root portion 23 is inclined toward the outer surface of the tubular body 10 to facilitate the flow of the refrigerant to the inner cavity 25.
  • the lateral fins 21 located on both sides of the wing root portion 23 are symmetrically inclined toward the outer surface of the tubular body 10, and the cross-sectional shape of the wing root portion 23 combined with the lateral fin portions 21 on both sides of the top portion thereof is similar to "umbrella". Shape (as shown in Figure 6) to facilitate the flow of refrigerant to the inner chamber 25.
  • the transverse fins 21 located on either side of the wing root 23 are horizontally disposed.
  • the first section of the convex portion of the serrated fin top 22 is trapezoidal, triangular or rectangular, the first section being substantially perpendicular to the axis of the tubular body 10.
  • the second section of the convex portion of the serrated fin top 22 is rectangular, parallelogram or trapezoidal, and the second section is substantially parallel to the axis of the tubular body 10. As shown in FIG. 5, when the second cross section is rectangular, ⁇ 1 is 90 degrees, and when the second cross section is parallelogram or trapezoid, ⁇ 1 may be an acute angle or an obtuse angle.
  • the recess of the serrated fin top 22 is trapezoidal, triangular or rectangular.
  • the fin top 22 is provided with at least one of a spike 221 (shown in Figure 6) and a second recess 222 (shown in Figure 7).
  • At least one side of the fin top 22 is provided with a spike 221 for increasing the heat exchange area of the fin top 22, which is advantageous for puncturing the liquid film during the condensing condition and accelerating the drainage of the condensed liquid.
  • At least one side of the fin top 22 is provided with a second groove 222 for increasing the heat exchange area of the fin top 22, diluting the liquid film, and enhancing the condensation performance.
  • the second grooves 222 may be provided on both sides of the fin top 22 or on the top of the fin top 22.
  • the number of projections of the serrated fin top 22 is 40 to 95 in the region of the fin 20 along the circumference of the tubular body 10 to enhance the condensation heat transfer effect.
  • the horizontal fin portion 21 is provided with a plurality of slits 211, and each slit 211 is connected with a concave portion of the serrated fin top 22, and the number of the slits is 40 to 95 to enhance the evaporation effect, which is advantageous for the refrigerant replenishment and The discharge of gaseous refrigerant.
  • the outer surface of the tube at the same time strengthening the body 10 is provided with a thread 14, the center line tangent to the tubular body 14 of the screw 10 the angle ⁇ 2 of 15 ° ⁇ 65 ° (As shown in Fig. 3), that is, the helix angle ⁇ 2 is 15° to 65°; it is used to increase the disturbance intensity on the side of the coolant, and the increase in the helix angle can increase the heat exchange area.
  • the increase in the number of threads is mainly used to increase the heat exchange area, while increasing the disturbance intensity of the inner brine and strengthening the inner heat exchange.
  • the inner side of the tubular body 10 is rolled using a slotted core to form a helically convex internal threaded structure.
  • the fins 20 are helically distributed along the surface of the tubular body 10; the single helix is distributed more evenly and the fins are more consistent.
  • the bottom of the raised portion of the serrated fin top 22 is split-like to facilitate processing and refrigerant flow.
  • the fins 20 on the heat exchange tubes are machined using a special fin roll mill, and are formed by an extrusion molding chipless process using a tool combination and a core slotting die, both sides. Strengthening at the same time. Since the refrigerant side of the heat exchange tube requires a relatively high degree of cleanliness, the chip-free processing by extrusion molding can avoid the occurrence of copper chips. Moreover, since the extrusion molding is self-contained, the strength is relatively high.
  • the thickness of the fins 20 is too thin, which is disadvantageous for rolling on both sides of the fins 20 to form the transverse fins 21.
  • the fins 20 are too thick, and the fins 20 extend to both sides, resulting in a relatively small cavity or even a congestion condition. Not conducive to the formation of evaporation chamber.
  • the tube 10 having an outer diameter of 19.05 mm and a wall thickness of 1.15 mm is processed.
  • the composite mold is used to extrude a certain spiral protrusion structure (fin 20) on the basis of the pipe body 10, and the extruded convex structure is rolled by a cutter combination and formed into a zigzag shape at the wing top 22, Increasing the surface area of the heat exchange tube facilitates the uneven surface shape formed by the knurling, and promotes the movement of the condensation; the second is to reduce the thickness of the refrigerant liquid film.
  • a natural crack is formed at the bottom of the serrated wing top 22.
  • the fins While the spiral fin is pressed, the fins are pressed on both sides to form a transverse fin portion 21 extending into the fin groove.
  • a 0.1 mm spacer is placed between the adjacent lateral fin portions 21 to form a gap 26, and the passage between the fins and the fins is used to discharge the liquid to enhance the condensation effect.
  • the slit 211 is naturally formed while the extrusion fin extends into the groove (both sides of the fin).
  • the heat exchange tubes operate as follows.
  • the heat exchange tube is used as an evaporation tube under refrigeration conditions: the liquid refrigerant outside the tube body 10 is mainly evaporated in the inner chamber 25, and first the liquid refrigerant enters the inner chamber 25 from the outer chamber 24 via at least one of the gap 26 and the slit 211.
  • the surface of the tube 10 at the bottom of the inner chamber 25 has a high surface temperature and has the superheat degree required for evaporation.
  • the surface of the tube body 10 at the bottom of the inner chamber 25 has a plurality of first grooves 251, which increases the roughness of the root portion.
  • the saturated liquid refrigerant evaporates in the inner cavity 25 having a certain degree of superheat and a large amount of vaporization core, and a large amount of bubbles generated by evaporation pass through at least one of the gap 26 and the slit 211
  • the liquid is discharged while the liquid refrigerant in the inner chamber 25 is also replenished by at least one of the gap 26 and the slit 211.
  • the heat exchange tube is used as a condensing tube under heating conditions: the high pressure gaseous refrigerant outside the tube is mainly condensed in the outer chamber 24, and the serrated fin top 22 on the fin 20 is extruded, so that the convex portions of the fin top 22 are both sides It is sharper and helps to pierce the bubbles of the refrigerant, so that the gaseous refrigerant quickly condenses into a liquid state.
  • the recessed portion of the fin top 22 and the transverse fin portion 21 inclined toward the inner surface of the tubular body 10 significantly increase the surface area of the outer chamber 24, which is particularly advantageous for condensation heat transfer of the gaseous refrigerant.
  • the transverse fin portion 21 Since the transverse fin portion 21 is inclined or curved, the liquid refrigerant generated by the condensation thereof flows downward under the combined action of surface tension and gravity, and is discharged to the inner cavity through at least one of the gap 26 and the slit 211 in time. 25, for further cooling, because the inner cavity 25 is connected to the ring, finally accumulating a certain amount of liquid refrigerant exits the heat exchange tube surface through the lowermost portion of the heat exchange tube.
  • Some embodiments provide a heat exchanger that includes the heat exchange tubes described above.
  • Some embodiments provide a heat pump assembly that includes the heat exchanger described above.
  • the use of the above heat exchanger can improve the energy efficiency of the heat pump unit.
  • the heat pump unit is a flooded heat pump unit.
  • the condensation process converts the gaseous refrigerant into a liquid refrigerant, diluting the liquid film as much as possible, and simultaneously guiding the liquid refrigerant away, so that the condensation process can continue to operate efficiently, otherwise the condensation performance will be attenuated.
  • the evaporation process converts the liquid refrigerant into a gaseous refrigerant, which is required to provide more vaporization cores, and the refrigerant can be wetted on the surface of the heat exchange tubes to improve heat exchange performance.
  • the heat exchange tubes and heat exchangers provided by some embodiments of the present disclosure can meet the needs of the heat pump unit for cooling and heating when the operating conditions are adjusted.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

一种换热管、换热器及热泵机组，其中换热管包括管体(10)和设于管体(10)外表面的翅片(20)；翅片(20)包括：翅根部(23)，设于管体(10)的外表面；横翅部(21)，设于翅根部(23)的顶部，且向翅根部(23)的两侧延伸；和翅顶部(22)，设于横翅部(21)的顶部，被构造成锯齿状，且锯齿状中的凹部延伸至横翅部(21)。换热管利于扩大翅顶部(22)的换热面积，摊薄液膜，且锯齿状的翅顶部(22)利于冷媒流动，提高冷凝性能；横翅部(21)向翅片(20)的两侧延伸，形成利于蒸发和冷凝的下层通道和上层通道，使换热管兼顾蒸发性能和冷凝性能。

Description

换热管、换热器及热泵机组
本申请是以CN申请号为201810409402.5，申请日为2018年5月2日的申请为 基础，并主张其优先权，该CN申请的公开内容在此作为整体引入本申请中。
技术领域
本公开涉及空气调节领域，尤其涉及一种换热管、换热器及热泵机组。
背景技术
满液式热泵机组用换热器，因其功能和工作原理不同，分为满液式蒸发器和满液式冷凝器，为两种不同结构形式的换热器。同样，作为满液式换热器的核心元器件换热管也分为满液式蒸发管和满液式冷凝管。
基于热泵机组对换热器既能蒸发又能冷凝的功能要求，需要对换热器结构进行重新设计和调整，以获得既能满足蒸发又能同时满足冷凝的换热器结构类型。而作为换热器当中蒸发冷凝两用的换热管的开发成为机组开发的一个瓶颈。
因此，需要开发一种既能满足蒸发又能同时满足冷凝功能的换热管。
发明内容
本公开一些实施例的目的之一是提出一种兼顾蒸发和冷凝的换热管、换热器及热泵机组。
依据本公开的一些实施例的一个方面，换热管包括管体和设于所述管体外表面的翅片；所述翅片包括：翅根部，设于所述管体的外表面；横翅部，设于所述翅根部的顶部，且向所述翅根部的两侧延伸；和翅顶部，设于所述横翅部的顶部，被构造成锯齿状，且所述锯齿状中的凹部延伸至所述横翅部。
在一些实施例中，所述翅片螺旋或平行设于所述管体的外表面，所述翅片间形成通道，所述通道内的相邻的所述横翅部之间具有间隙。
在一些实施例中，所述翅片螺旋或平行设于所述管体的外表面，所述横翅部将所述翅片间形成的通道分为外腔和内腔，所述内腔相对于所述外腔靠近所述管体的外表面。
在一些实施例中，所述内腔的壁面上设有第一凹槽。
在一些实施例中，所述第一凹槽设于所述管体的外表面。
在一些实施例中，所述第一凹槽呈“工”字型、“十”字型、“X”型、“U”型、三角形或三边以上的多边形。
在一些实施例中，所述横翅部被构造成曲线型，或者，所述横翅部的表面被构造成曲线型。
在一些实施例中，所述横翅部设有多个狭缝，至少一个所述狭缝连接至所述锯齿状的一凹部。
在一些实施例中，每一所述狭缝对应连接至所述锯齿状的一凹部。
在一些实施例中，至少位于所述翅根部一侧的所述横翅部向所述管体的外表面方向倾斜。
在一些实施例中，位于所述翅根部两侧的所述横翅部对称的向所述管体的外表面方向倾斜。
在一些实施例中，所述锯齿状的凸部的第一截面呈梯形、三角形或矩形，所述第一截面大体上垂直于所述管体的轴线。
在一些实施例中，所述锯齿状的凸部的第二截面呈矩形、平行四边形或梯形，所述第二截面大体上平行于所述管体的轴线。
在一些实施例中，所述锯齿状的凹部呈梯形、三角形或矩形。
在一些实施例中，所述翅顶部的至少一侧设有尖刺和第二凹槽中的至少一种。
在一些实施例中，在所述翅片沿所述管体的一周的区域段上，所述锯齿状的凸部数量为40～95个。
在一些实施例中，所述管体的内表面设有螺纹，所述螺纹的切线与所述管体的中心线的夹角为15°～65°。
本公开一些实施例提供了一种换热器，其包括上述的换热管。
本公开一些实施例提供了一种热泵机组，其包括上述的换热器。
在一些实施例中，所述热泵机组为满液式热泵机组。
根据本公开的一些实施例的换热管，其包括管体和设于管体外表面的翅片；翅片包括翅根部、横翅部和翅顶部，翅顶部设于横翅部的顶部，被构造成锯齿状，且锯齿状中的凹部延伸至横翅部，利于扩大翅顶部的换热面积，摊薄液膜，且锯齿状的翅顶部利于冷媒流动，提高冷凝性能；横翅部向翅片的两侧延伸，形成利于蒸发和冷凝的下层通道和上层通道，使换热管兼顾蒸发性能和冷凝性能。
附图说明
图1是示出根据本公开一些实施例的换热管的整体示意图；
图2是示出根据本公开一些实施例的换热管的局部示意图；
图3是示出根据本公开一些实施例的换热管的剖视示意图；
图4是示出根据本公开一些实施例的换热管的局部放大示意图；
图5是示出根据本公开一些实施例的换热管的翅片的局部放大示意图；
图6是示出根据本公开一些实施例的换热管的局部侧视示意图；
图7是示出根据本公开一些实施例的换热管的翅片的局部放大示意图。
附图中标号说明：
10-管体；11-光滑段；12-过渡段；13-成翅段；14-螺纹；
20-翅片；
21-横翅部；211-狭缝；
22-翅顶部；221-尖刺；222-第二凹槽；
23-翅根部；
24-外腔；
25-内腔；251-第一凹槽；
26-间隙。
具体实施方式
下面将结合本公开实施例中的附图，对实施例中的技术方案进行清楚、完整地描述。显然，所描述的实施例仅仅是本公开的一部分实施例，而不是全部的实施例。基于本公开的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本公开保护的范围。
在本公开的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“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公开和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本公开保护范围的限制。
如图1所示，在一些实施例中，换热管包括管体10，管体10包括未加工的光滑 段11，沿圆周完全成翅的成翅段13，以及光滑段11与成翅段13之间的过渡段12。
在一些实施例中，光滑段11用于壳管与换热管之间的胀接和密封。换热管在机组内运行时，长时间保持在震动状态，过渡段12用于提高换热管的强度。过渡段12的外径小于光滑段11的外径。
如图2所示，在一些实施例中，换热管包括管体10和设于管体10外表面的翅片20。翅片20设于管体10的成翅段13。
在一些实施例中，翅片20为螺旋翅片，沿管体10的轴向螺旋设于管体10。
在一些实施例中，翅片20包括多个环形翅片，单个环形翅片沿管体10的圆周向设置，且各环形翅片沿管体10的轴向间隔布置。进一步地，各环形翅片平行设置。
在一些实施例中，翅片20包括多个直线型翅片，单个直线型翅片的长度方向与管体10的轴向一致，各直线型翅片沿管体10的圆周向间隔布置。进一步地，各直线型翅片平行设置。
如图4所示，在一些实施例中，翅片20包括翅根部23、横翅部21和翅顶部22。
在一些实施例中，翅根部23设于管体10的外表面。
在一些实施例中，横翅部21设于翅根部23的顶部，且向翅根部23的两侧延伸。横翅部21下方与翅根部23和管体10的外表面形成利于提高蒸发性能的空间。
在一些实施例中，翅顶部22设于横翅部21的顶部，被构造成锯齿状，且翅顶部22的锯齿状中的的凹部延伸至横翅部21，用于扩大翅顶部22的换热面积，摊薄液膜，且锯齿状的翅顶部22利于冷媒流动，提高冷凝性能。
在一些实施例中，翅顶部22的厚度小于翅根部22的厚度，利于在翅顶部22形成尖锐边缘，刺破携液的气态冷媒。
在一些实施例中，翅片20的顶部采用挤压方式形成翅顶部22，翅顶部22的厚度相对于翅根部23的厚度薄，横翅部21相对于翅根部23和翅顶部22向翅片20的两侧延伸。
如图2、图4所示，在一些实施例中，翅顶部22被构造成锯齿状，且锯齿状中的凹部延伸至横翅部21，横翅部21向翅片20的两侧延伸，该结构兼顾蒸发性能和冷凝性能，缓解了常规冷凝管用作蒸发管时的性能衰减问题；以及缓解了常规蒸发管用作冷凝管时的性能衰减问题。
如图4所示，在一些实施例中，翅片20螺旋或平行设于管体10的外表面，螺旋翅片的本体间形成通道，或者多个翅片的相邻翅片间形成通道，通道内的相邻的横翅 部21之间具有间隙26。
在一些实施例中，沿横翅部2的延伸方向，通道内的相邻的横翅部21之间具有间隙26。
在一些实施例中，沿横翅部2的延伸方向，通道内的相邻的横翅部21之间具有重叠段，间隙26位于相邻横翅部21的在翅片高度方向的空间。进一步地，其中一个横翅部21在翅片高度方向高于与其相邻的横翅部21。或者，其中一个横翅部21的末端(重叠段部位)在翅片高度方向高于与其相邻的横翅部21的末端(重叠段部位)。
在一些实施例中，通道内的相邻的横翅部21之间具有间隙26，打通了翅与翅之间的上下层通道，利于液态冷媒流通，强化了冷凝效果；并且在对冷媒进行蒸发时，利于冷媒的补充和气态冷媒的排出，强化了蒸发功能；利于蒸发和冷凝两种性能均不衰减。
在一些实施例中，翅片20螺旋或平行设于管体10的外表面，横翅部21将翅片20间形成的通道分为外腔24和内腔25，内腔25相对于外腔24靠近管体10的外表面。
在一些实施例中，横翅部21将翅片20间形成的通道分为外腔24和内腔25，通道内的相邻的横翅部21之间具有间隙26，间隙26利于保证下层蒸发功能形成的蒸发气泡逸出；且利于冷媒冷凝时，液态冷媒的排出。内腔25由横翅部21、翅根部23和管体10的外表面围成，主要是形成利于蒸发的小腔，采用的原理主要是泡核沸腾的原理。外腔25由横翅部21和翅顶部22围成，主要是增大换热面积，摊薄液膜，利于冷凝。因此，利于实现蒸发和冷凝两种性能均不衰减。
在一些实施例中，内腔25的壁面上设有第一凹槽251，通过设置第一凹槽251使内腔25内的表面粗糙不平，利于形成蒸发所需要的汽化核心，强化蒸发换热。
在一些实施例中，第一凹槽251可以设于管体10的外表面。由于管体10内通入载冷剂，用于与管体10外的冷媒换热，将第一凹槽251设于管体10的外表面，利于在管体10外表面形成汽化核心，强化蒸发换热；再者可以在原有平滑的管体10的外表面的基础上增加换热面积。进一步地，管体10的外表面，沿翅片20间的通道方向设有多个第一凹槽251。
在一些实施例中，利用平滑的滚光轮在管体10的外表面进行滚光压平处理，这样在管体10的外表面可以形成多坑表面结构，以提供蒸发所需要的汽化核心，强化蒸发换热。
在一些实施例中，第一凹槽251可以设于翅根部23的表面，利于形成汽化核心。 进一步地，第一凹槽251可以沿翅根部23的高度方向设置，以利于冷媒沿第一凹槽251的流动。
在一些实施例中，第一凹槽251呈“工”字型、“十”字型、“X”型、“U”型、圆形、三角形、四边形、大于四边的多边形，或者其他不规则或规则的形状等。
在内腔25设置多个第一凹槽251，不平结构利于增加内腔25的粗糙度，利于形成汽化核心，强化蒸发功能。
在一些实施例中，横翅部21被构造成曲线型，或者，横翅部21的表面被构造成曲线型。横翅部21本体或表面被构造成曲线型利于增大换热面积，摊薄液膜，且利于冷媒的流动。
在一些实施例中，横翅部21设有利于流体穿过的狭缝211，利于冷媒的补充和蒸发气泡的逸出。
在一些实施例中，横翅部21设有多个狭缝211，每一狭缝211对应连接至翅顶部22的锯齿状的一凹部。通过设置狭缝211利于冷媒的流动，且狭缝211连接至翅顶部22的凹部利于冷媒流向内腔25。
在一些实施例中，狭缝211可以是长条形，且沿横翅部21的延伸方向延伸。
在一些实施例中，横翅部21设有多个圆形、三角形、方形，或者多于四个边的多边形，或者其他规则或不规则的通孔，以利于冷媒流向内腔25或气态冷媒的排出。
在一些实施例中，至少位于翅根部23一侧的横翅部21向管体10的外表面方向倾斜，以利于冷媒流向内腔25。
在一些实施例中，位于翅根部23两侧的横翅部21对称的向管体10的外表面方向倾斜，翅根部23与其顶部两侧的横翅部21结合的截面形状类似为“伞”状(如图6所示)，以利于冷媒流向内腔25。
在一些实施例中，位于翅根部23两侧的横翅部21水平设置。
在一些实施例中，锯齿状的翅顶部22的凸部的第一截面呈梯形、三角形或矩形，第一截面大体上垂直于管体10的轴线。
在一些实施例中，锯齿状的翅顶部22的凸部的第二截面呈矩形、平行四边形或梯形，第二截面大体上平行于管体10的轴线。如图5所示，在第二截面呈矩形时，β 1为90度，在第二截面呈平行四边形或梯形时，β 1可以为锐角或钝角。
在一些实施例中，锯齿状的翅顶部22的凹部呈梯形、三角形或矩形。
在一些实施例中，翅顶部22设有尖刺221(如图6所示)和第二凹槽222(如图 7所示)中的至少一种。
进一步地，翅顶部22的至少一侧设有尖刺221，尖刺221用于增大翅顶部22的换热面积，冷凝工况时有利于刺破液膜，加快排走冷凝液体。翅顶部22的至少一侧设有第二凹槽222，第二凹槽222用于增大翅顶部22的换热面积，摊薄液膜，强化冷凝性能。进一步地，第二凹槽222可以设于翅顶部22的两侧，或者，设于翅顶部22的顶部。
在一些实施例中，在翅片20沿管体10的一周的区域段上，锯齿状的翅顶部22的凸部数量为40～95个，以强化冷凝换热效果。
进一步地，横翅部21设有多条狭缝211，每一狭缝211与锯齿状的翅顶部22的一凹部对应连接，狭缝的数量40～95，以强化蒸发效果，利于冷媒补充和气态冷媒的排出。
在一些实施例中，在强化管体10的外表面的同时，管体10的内表面设有螺纹14，螺纹14的切线与管体10的中心线的夹角β 2为15°～65°(如图3所示)，也就是螺旋角β 2为15°～65°；用于增加载冷剂侧的扰动强度，同时螺旋角增加可以增加换热面积。
在一些实施例中，管体10内侧的螺纹14沿周向成多头均布，螺纹头数n＝30～65。螺纹头数增加主要是用于增加换热面积，同时增加内侧载冷剂的扰动强度，强化内侧换热。
在一些实施例中，管体10的内侧利用开槽的衬芯滚压形成螺旋状凸起的内螺纹结构。
在一些实施例中，翅片20沿管体10表面呈单头螺旋分布；单螺旋分布成翅更加均匀，翅片一致性更好。
在一些实施例中，锯齿状的翅顶部22的凸部底部呈裂口状，利于加工和冷媒流动。
在一些实施例中，换热管上的翅片20采用专门的翅片辊轧机进行加工，采用挤压成型无屑加工工艺，利用刀具组合和衬芯开槽模具进行辊轧而成，双侧强化同时进行。由于换热管冷媒侧要求清洁度比较高，采用挤压成型无屑加工，可以避免产生铜屑。再者，由于挤压成型自成一体，强度也比较高。
在一些实施例中，翅片与翅片之间形成的通道宽度h 1＝0.254mm～0.558mm，能够兼顾上层冷凝效果。如果间隙过小，下层蒸发腔体容易出现堵塞，同时上层冷凝凝结 之后的液体不利于排出，降低冷凝效果。
在一些实施例中，如图3所示，翅片20的厚度h 2＝0.15mm～0.305mm。翅片20厚度过薄，不利于在翅片20的两侧进行滚压形成横翅部21，翅片20过厚，翅片20向两侧延伸会造成腔体比较小，甚至出现拥堵状况，不利于蒸发腔体的形成。
在一具体实施例中，采用外径19.05mm，壁厚为1.15mm的管体10进行加工。利用组合模具在管体10基础上先挤压成一定螺旋凸起的结构(翅片20)，利用刀具组合对挤压成的凸起结构进行滚压并在翅顶部22形成锯齿状，一是增加换热管的表面积，利于滚花形成的凸凹不平的外表面形状，促进冷凝的移动；二是减小冷媒液膜的厚度。同时由于加工引起形变，在锯齿状的翅顶部22的底部形成自然裂口。螺旋翅片进行挤压的同时，在翅片两侧进行挤压形成向翅槽内延伸的横翅部21。同时相邻横翅部21中间放置0.1mm垫片形成间隙26，利用翅与翅之间的通道进行排液，强化冷凝效果。同时因翅片顶部先挤压形成锯齿状，在挤压翅片向槽内(翅片两侧)延伸的同时自然形成狭缝211。
在一些实施例中，换热管的工作原理如下。
换热管在制冷工况下作为蒸发管使用：管体10外侧液态冷媒主要在内腔25进行蒸发，首先液态冷媒由外腔24经由间隙26和狭缝211中的至少一种进入内腔25，内腔25底部的管体10表面温度较高，具备蒸发所需要的过热度；同时内腔25底部的管体10表面具有多个第一凹槽251，增大了翅根部位的粗糙度，并在翅根部位形成大量蒸发所需的汽化核心；饱和液态冷媒在具有一定过热度和大量汽化核心的内腔25进行蒸发，蒸发产生的大量气泡通过间隙26和狭缝211中的至少一种排出，同时内腔25内的液态冷媒也通过间隙26和狭缝211中的至少一种进行补充。
换热管在采暖工况下作为冷凝管使用：管外侧高压气态冷媒主要在外腔24进行凝结，翅片20上的锯齿状的翅顶部22通过挤压成型，使得翅顶部22的凸部两侧比较尖锐，有利于刺破冷媒气泡，使得气态冷媒快速凝结为液态。翅顶部22的凹部及向管体10内表面倾斜的横翅部21显著增大了外腔24的表面积，这尤为利于气态冷媒的凝结换热。
由于横翅部21是倾斜的或者弯曲的，其上凝结产生的液态冷媒在表面张力及其重力综合作用下向下流动，并及时经过间隙26和狭缝211中的至少一种排至内腔25，进行进一步的冷却，由于内腔25环向连通，最终积累到一定量的液态冷媒经过换热管最下方排出换热管表面。
一些实施例提供了一种换热器，其包括上述的换热管。
一些实施例提供了一种热泵机组，其包括上述的换热器。采用上述换热器能够提高热泵机组的能效。
在一些实施例中，热泵机组为满液式热泵机组。
在满液式热泵机组当中，蒸发和冷凝工作原理和功能均不相同，在工作当中是两个相反的过程。冷凝过程是气态冷媒转换成液态冷媒，尽可能摊薄液膜，同时将液态冷媒及时导走，以便该冷凝过程能够持续高效运行，否则冷凝性能会衰减。而蒸发过程将液态冷媒转换成气态冷媒，要求能够提供更多的汽化核心，冷媒能够在换热管表面湿润，提高换热性能。
本公开一些实施例提供的换热管和换热器能够满足热泵机组在工况调整时对制冷和制热的需要。
在本公开的描述中，需要理解的是，使用“第一”、“第二”、“第三”等词语来限定零部件，仅仅是为了便于对上述零部件进行区别，如没有另行声明，上述词语并没有特殊含义，因此不能理解为对本公开保护范围的限制。
最后应当说明的是:以上实施例仅用以说明本公开的技术方案而非对其限制；尽管参照较佳实施例对本公开进行了详细的说明，所属领域的普通技术人员应当理解：依然可以对本公开的具体实施方式进行修改或者对部分技术特征进行等同替换；而不脱离本公开技术方案的精神，其均应涵盖在本公开请求保护的技术方案范围当中。

Claims (20)

  1. 一种换热管，其中，包括管体(10)和设于所述管体(10)外表面的翅片(20)；
    所述翅片(20)包括：
    翅根部(23)，设于所述管体(10)的外表面；
    横翅部(21)，设于所述翅根部(23)的顶部，且向所述翅根部(23)的两侧延伸；和
    翅顶部(22)，设于所述横翅部(21)的顶部，被构造成锯齿状，且所述锯齿状中的凹部延伸至所述横翅部(21)。
  2. 如权利要求1所述换热管，其中，所述翅片(20)螺旋或平行设于所述管体(10)的外表面，所述翅片(20)间形成通道，所述通道内的相邻的所述横翅部(21)之间具有间隙(26)。
  3. 如权利要求1所述的换热管，其中，所述翅片(20)螺旋或平行设于所述管体(10)的外表面，所述横翅部(21)将所述翅片(20)间形成的通道分为外腔(24)和内腔(25)，所述内腔(25)相对于所述外腔(24)靠近所述管体(10)的外表面。
  4. 如权利要求3所述的换热管，其中，所述内腔(25)的壁面上设有第一凹槽(251)。
  5. 如权利要求4所述的换热管，其中，所述第一凹槽(251)设于所述管体(10)的外表面。
  6. 如权利要求4所述的换热管，其中，所述第一凹槽(251)呈“工”字型、“十”字型、“X”型、“U”型、三角形或三边以上的多边形。
  7. 如权利要求1所述的换热管，其中，所述横翅部(21)被构造成曲线型，或者，所述横翅部(21)的表面被构造成曲线型。
  8. 如权利要求1所述的换热管，其中，所述横翅部(21)设有多个狭缝(211)，至少一个所述狭缝(211)连接至所述锯齿状的一凹部。
  9. 如权利要求8所述的换热管，其中，每一所述狭缝(211)对应连接至所述锯齿状的一凹部。
  10. 如权利要求1所述的换热管，其中，至少位于所述翅根部(23)一侧的所述横翅部(21)向所述管体(10)的外表面方向倾斜。
  11. 如权利要求10所述的换热管，其中，位于所述翅根部(23)两侧的所述横翅部(21)对称的向所述管体(10)的外表面方向倾斜。
  12. 如权利要求1所述的换热管，其中，所述锯齿状的凸部的第一截面呈梯形、三角形或矩形，所述第一截面垂直于所述管体(10)的轴线。
  13. 如权利要求1所述的换热管，其中，所述锯齿状的凸部的第二截面呈矩形、平行四边形或梯形，所述第二截面平行于所述管体(10)的轴线。
  14. 如权利要求1所述的换热管，其中，所述锯齿状的凹部呈梯形、三角形或矩形。
  15. 如权利要求1所述的换热管，其中，所述翅顶部(22)的至少一侧设有尖刺(221)和第二凹槽(222)中的至少一种。
  16. 如权利要求1所述的换热管，其中，在所述翅片(20)沿所述管体(10)的一周的区域段上，所述锯齿状的凸部数量为40～95个。
  17. 如权利要求1所述的换热管，其中，所述管体(10)的内表面设有螺纹(14)，所述螺纹(14)的切线与所述管体(10)的中心线的夹角为15°～65°。
  18. 一种换热器，其中，包括如权利要求1～17任一项所述的换热管。
  19. 一种热泵机组，其中，包括如权利要求18所述的换热器。
  20. 如权利要求19所述的热泵机组，其中，所述热泵机组为满液式热泵机组。
PCT/CN2018/121202 2018-05-02 2018-12-14 换热管、换热器及热泵机组 WO2019210690A1 (zh)

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CN110108148A (zh) * 2019-05-29 2019-08-09 珠海格力电器股份有限公司 换热管及设有其的空调器
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