WO2014012286A1 - Ensemble refroidisseur équipé d'un condenseur évaporatif à serpentin de couplage avec matériau de remplissage - Google Patents

Ensemble refroidisseur équipé d'un condenseur évaporatif à serpentin de couplage avec matériau de remplissage Download PDF

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Publication number
WO2014012286A1
WO2014012286A1 PCT/CN2012/080018 CN2012080018W WO2014012286A1 WO 2014012286 A1 WO2014012286 A1 WO 2014012286A1 CN 2012080018 W CN2012080018 W CN 2012080018W WO 2014012286 A1 WO2014012286 A1 WO 2014012286A1
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WO
WIPO (PCT)
Prior art keywords
heat exchange
coil
pipe
compressor
evaporative condenser
Prior art date
Application number
PCT/CN2012/080018
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English (en)
Chinese (zh)
Inventor
李志明
Original Assignee
广州市华德工业有限公司
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Publication of WO2014012286A1 publication Critical patent/WO2014012286A1/fr

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Classifications

    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • 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
    • F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
    • F28D5/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F25/00—Component parts of trickle coolers
    • F28F25/02—Component parts of trickle coolers for distributing, circulating, and accumulating liquid
    • F28F25/08—Splashing boards or grids, e.g. for converting liquid sprays into liquid films; Elements or beds for increasing the area of the contact surface
    • F28F25/087—Vertical or inclined sheets; Supports or spacers
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02732—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two three-way valves
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02791—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using shut-off valves
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/041—Details of condensers of evaporative condensers

Definitions

  • the invention relates to the field of air conditioning equipment, in particular to a chiller of a coil evaporative condenser.
  • Evaporative condenser to release heat into the outdoor air and applied to the chiller is an important way to achieve efficient, stable cooling, compared with water-cooled condensers and air-cooled condensers, its heat transfer efficiency is high, Has significant energy saving and emission reduction prospects.
  • the coil for evaporative condenser used in the chiller on the market is a transverse coil, which is cooled by spraying water on the outer surface of the coil, and uses circulating spray water to evaporate the air to remove heat.
  • the coil Since the cooling wind direction is perpendicular to the coil (that is, the cooling air passes through the plane space formed by each heat exchange tube and is perpendicular to the straight pipe section of the heat exchange tube), the coil has a windward side and a leeward side, and the leeward side Lack of air convection heat transfer reduces coil heat transfer efficiency.
  • the effective heat exchange area of the transverse coil is small, the length of the coil to be used needs to be increased. The same as the H inch, due to the misalignment between the tubes and the tubes of the conventional transverse coil, there is no mechanical cleaning operation space, and there is also The disadvantage of being difficult to clean. Therefore, the lack of lateral coils greatly limits the use of evaporative condensers in chillers.
  • the purpose of the present invention is to overcome the shortcomings of the prior art and to provide a chiller for a coil evaporative condenser which can improve heat exchange efficiency.
  • a chiller with a packed coupling coil evaporative condenser comprising a compressor, an evaporative condenser, a throttling device and an evaporator;
  • the evaporative condenser comprises a coil heat exchanger, a fan, a water distributor and
  • the coil heat exchanger is composed of a plurality of heat exchange fins connected through an inlet header and an outlet header;
  • the heat exchange fin includes a coil and a filler, and the coil is provided with at least one piece
  • the spray cooling water is guided to flow from the upper heat exchange tube to the packing of the lower heat exchange tube.
  • the coil is longitudinally disposed, that is, the cooling wind blown by the fan is along the straight tube of the coil
  • the heat exchange tubes of the coil are S-shaped, and the filler is disposed between the adjacent heat exchange tubes to connect the heat exchange tubes into a continuous water flow surface.
  • the straight pipe sections adjacent to the heat exchange tubes are parallel to each other, and the pipe spacing of the straight pipe sections adjacent to the heat exchange pipes is the same, or the pipe spacing is from the upper layer receiving the spray cooling water to the shower cooling.
  • the lower layer of water gradually becomes smaller.
  • the exhaust port of the compressor is connected to the gas pipe of the evaporative condenser, and the liquid pipe of the evaporative condenser is connected to the liquid pipe of the evaporator through the throttling device, and the gas pipe of the evaporator and the suction of the compressor The port is connected, so the chiller has a refrigeration cycle mode.
  • the chiller is provided with a four-way valve, and the four ports of the four-way directional valve are respectively connected with a compressor vent, a gas pipe of an evaporative condenser, a gas pipe of an evaporator, and a compressor.
  • the suction port is connected.
  • the working principle of the invention When in the refrigeration cycle mode, the refrigerant is compressed by the compressor to a high temperature The gas in the pressurized state enters the evaporative condenser from the refrigeration system pipeline. After the evaporative condenser, the gas in the high temperature and high pressure state is cooled into a low temperature and high pressure liquid, and the low temperature and low pressure liquid is formed into the evaporator and the chilled water through the throttling device.
  • the refrigerant liquid evaporates and vaporizes in the evaporator and is sucked away by the compressor to complete the refrigeration cycle mode; when the heat pump is in the circulation mode, the refrigerant is compressed by the compressor into a high temperature and high pressure state gas.
  • the refrigeration system pipeline enters the evaporator and exchanges heat with the low temperature hot water to prepare high temperature hot water.
  • the high temperature and high pressure gas is cooled into a low temperature and high pressure liquid, and the low temperature and low pressure liquid is formed by the throttling device into the evaporative condenser.
  • the refrigerant liquid evaporates and is sucked away by the compressor to complete the heat pump cycle mode.
  • the invention adopts a filler-coupled longitudinal serpentine coil evaporative condenser, which replaces the traditional air-cooling and water-cooling modes, and can further improve the heat exchange efficiency;
  • the elbows at both ends of the longitudinal coil are placed in the airflow and cooling water sprinkling space to improve the effective utilization area of the coil;
  • the evaporative condenser of the present invention adopts a filler-coupled longitudinal serpentine coil, so that the cooling water flows through the surface of the upper heat exchange tube and flows under the guidance of the filler to the surface of the lower heat exchange tube to guide the sowing water and reduce the cooling water.
  • the stay at the bottom of the heat exchange tube reduces the phenomenon that the cooling water drifts backward or floats under the blowing of the cooling air - and increases the surface area of the cooling water evaporating heat transfer, thereby improving the heat exchange efficiency and reducing the heat exchange tube.
  • the role of quantity is the role of quantity.
  • Figure i is a schematic diagram of the refrigeration cycle mode of the chiller of the present invention.
  • FIG. 2 is a schematic view of the principle of the chiller of the present invention.
  • Figure 3 is a schematic view showing the principle of the heat pump cycle mode of the chiller of the present invention.
  • FIG. 4 is a schematic view showing the principle of using a two-position three-way reversing valve for the chiller of the present invention
  • Figure 5 is a schematic view showing the principle of the four-way reversing enthalpy of the chiller of the present invention.
  • Figure 6 is a schematic structural view of Embodiment 1 of the evaporative condenser of the present invention.
  • Figure 7 is a partial cross-sectional view showing the AA of the evaporative condenser of the present invention.
  • Figure 8 is a schematic structural view of a heat exchange fin in the first embodiment of the evaporative condenser of the present invention
  • Figure 9 is a cross-sectional view of the heat transfer fin of the first embodiment of the evaporative condenser of the present invention; the cross-sectional direction corresponds to Figure 9 A-A direction;
  • Figure 10 is a cross-sectional view showing another heat exchange fin of the first embodiment of the evaporative condenser of the present invention; the cross-sectional direction corresponds to the A-A direction of Figure 9;
  • Figure 11 is a schematic structural view of a second embodiment of the evaporative condenser of the present invention.
  • Figure 12 is a schematic structural view of a heat exchange fin in the second embodiment of the evaporative condenser of the present invention
  • Figure 13 is a cross-sectional view taken along line A-A of the heat transfer fin shown in Figure 7;
  • Figure 4 is a schematic view showing another structure of the coil of the evaporative condenser of the present invention.
  • Figure! 5 is another structural schematic diagram of the coil of the evaporative condenser of the present invention.
  • Figure! 6 is a schematic cross-sectional view of the third embodiment of the evaporative condenser of the present invention.
  • Figure! 7 is a schematic structural view of the present invention in which a condenser fan is placed at the front of the heat exchanger;
  • Figure! 8 is a schematic structural view of the present invention in which a condenser fan is vertically placed;
  • FIG. 1 is a schematic view showing the principle of the refrigeration cycle mode of the chiller of the present invention.
  • the chiller comprises a compressor 1, an evaporative condenser 2, a throttling device 3 and an evaporator 4;
  • the exhaust port 7 is connected to the gas pipe 2a of the evaporative condenser, and the liquid pipe 2b of the evaporative condenser is connected to the liquid pipe 4a of the evaporator through a throttling device, the gas pipe 4b of the evaporator and the suction port 8 of the compressor. connection.
  • the evaporative condenser 2 employs a longitudinally disposed coil of filler packing, which is not described in detail first.
  • the working principle of the invention When the refrigerant is compressed by the compressor 1 into a high temperature and high pressure state, the refrigerant enters the evaporative condenser 2 through the pipeline of the refrigeration system, and after passing through the evaporative condenser 2, the gas in the high temperature and high pressure state is cooled to a low temperature. a high-pressure liquid, and through the throttling device 3 to form a low-temperature low-pressure liquid into the evaporator 4 The chilled water is subjected to heat exchange to obtain cold water, and then the refrigerant liquid is evaporated and vaporized in the evaporator 4 and sucked away by the compressor i to complete the refrigeration cycle mode;
  • the chiller is provided with a first cooling port 9, a second refrigerating valve 10, and a first heat pump valve 11. And a second heat pump valve 12; the first cooling width 9 is disposed on a connecting line of the exhaust port 7 of the compressor and the gas pipe 2a of the evaporative condenser, and the second cooling head 10 is disposed at the suction port 8 of the compressor
  • the first heat pump valve U is disposed on the connecting line of the exhaust port 7 of the compressor and the gas pipe 4b of the evaporator, and the second heat pump valve 12 is disposed in the compressor
  • the suction port 8 is connected to the gas pipe 2a of the evaporative condenser. Therefore, the chiller has a refrigeration cycle mode and a heat pump cycle mode.
  • the evaporative condenser 2 employs a longitudinally coupled coil of packing coupling.
  • the working principle of the invention When the heat pump is in the circulation mode, as shown in FIG. 3, the first heat pump valve 11 and the second heat pump valve 12 are opened at this time, and the first refrigerating valve 9 and the second refrigerating valve 10 are closed, the refrigerant After being compressed by the compressor 1 into a high-temperature and high-pressure gas, the refrigerant enters the evaporator 4 through the pipeline of the refrigeration system, exchanges heat with the low-temperature hot water, and obtains high-temperature hot water, and then the gas in the high-temperature and high-pressure state is cooled into a low-temperature high-pressure liquid.
  • the low-temperature low-pressure liquid is formed into the evaporative condenser 2 through the throttling device 3, and then the refrigerant liquid evaporates and vaporizes in the evaporative condenser 2 and is sucked away by the compressor 1, completing the heat pump circulation mode.
  • FIG. 4 is a schematic view showing the principle of using a two-position three-way reversing valve for the chiller of the present invention, which is different from the first embodiment in that the exhaust port 7 of the compressor 1 is provided with the first two positions.
  • the three-way reversing width is 13.
  • the suction port 8 of the compressor is provided with a second two-position three-way reversing width 14; the two outlets of the first two-position three-way reversing valve 13 are respectively connected with the gas pipe of the evaporative condenser 2a is connected to the gas pipe 4b of the evaporator, and the two inlets of the second two-position three-way reversing width 14 are respectively connected to the gas pipe 2a of the evaporative condenser and the gas pipe 4b of the evaporator.
  • the evaporative condenser 2 employs a longitudinally disposed coil of a packing coupling.
  • FIG. 5 is a schematic view showing the principle of the four-way reversing valve of the chiller of the present invention. Compared with the first embodiment, the difference is that the four ports of the four-way reversing flange 15 are respectively arranged with the row of the compressor. The gas port 7, the gas pipe 2a of the evaporative condenser, the gas pipe 4b of the evaporator, and the suction port 8 of the compressor are connected. Similarly, the evaporative condenser 2 employs a longitudinally disposed coil of filler packing. The evaporative condenser 2 used in the above embodiment will be described in detail below.
  • FIG. 6 and Figure 7 show the structure of the evaporative condenser 2 of the present invention, including a coil heat exchanger, a fan 21 -, a water pump 22, a water distributor 23, a sump 24 and a frame 25;
  • the heat exchange fins formed by the plurality of serpentine coils are connected by the inlet header 28 and the outlet header 29.
  • Each heat exchange fin includes a longitudinal serpentine (S-shaped) coil 26 and a packing 27 disposed between the planar spaces formed by the serpentine coils, and the packing and the coil form a tight fit structure, that is, the coupling therebetween Connected to form a segment structure.
  • the coil is longitudinally disposed, that is, the cooling wind blown by the fan flows along the approximate length direction of the straight pipe section of the coil (the two do not need to be completely parallel); basically, the cooling wind is from each heat exchange tube
  • the formed planar space is swept flat, and the coil 7 is provided with at least one piece of ffi for guiding the spray cooling water from the upper heat exchange tube to the lower layer heat exchange tube.
  • the serpentine coil 26 is formed by continuous S-shaped bending of the heat exchange tubes, wherein the straight sections of the heat exchange tubes 261 are substantially parallel.
  • the coil 26 can also be of other shapes that can be fitted with packing and suitable for use in an evaporative condenser.
  • the heat transfer tubes of the serpentine coil 26 may be copper tubes, stainless steel tubes or galvanized steel tubes, etc., and the internal flow passages have a circular, elliptical, spiral, corrugated, and olive shape.
  • the inner and outer surfaces of the serpentine coil 26 can adopt a smooth surface, preferably an enhanced heat transfer surface provided with internal and external threads, and the outer surface of the serpentine coil is provided with hydrophilic or anticorrosive. coating.
  • Each serpentine coil has an inlet and an outlet for the flow passage.
  • Figures 8 and 9 show the construction of the heat transfer fins, including the coil 26 and the packing 27, having a structure in which a piece of packing 27 is formed in continuous coupling with the coil 26.
  • the filler of the one piece corresponds to the heat exchange tube 261 of the corresponding position coil, and a plurality of grooves 271 matched with the size are provided for accommodating the heat exchange tubes.
  • the above-mentioned piece of filler 27 completely covers one side surface of the heat transfer tube of the coil 26.
  • the filler 27 is made of, but not limited to, a metal material such as rubber (PVC, PP, PE, etc.), paper or aluminum foil, or copper foil.
  • the filler 27 may be a flat plate filler having a smooth surface or a single or multi-directional corrugated filler; the cross-sectional shape may be wavy, rectangular or oblong, wherein it is preferred that the filler be formed on one or both sides of the filler.
  • the convex and concave surface is formed to facilitate the flow of the spray cooling water, and the residence time of the cooling water on the surface of the filler is increased, and the evaporation heat exchange area is correspondingly increased.
  • the packing 27 is two sheets, and is fitted to the both side surfaces of the serpentine coil in a snap-fit manner to form a continuous coupling form.
  • the two pieces of filler 27 can enclose the heat exchange tube 261 of the coil, or leave a certain gap at the joint of the two sheets of filler 27, as shown in Fig. 10, the slit can make a cooling water flow through the heat exchange tube surface.
  • the high temperature fluid enters the serpentine coil 26 through the mouthpiece header 28, at which time the water pump 22 delivers the low temperature water in the sump 24 to the water distributor 23 at the top of the serpentine coil, which is sprayed through the nozzle to the serpentine shape.
  • the outer surface of the coil forms a very thin water film.
  • the fan 21 introduces the wind with a lower temperature and relative humidity into the space where the evaporative condenser is located, and the heat exchanger and the heat exchanger and the filler 27
  • the cooling water is sufficiently heat-exchanged, part of the water in the water film absorbs heat and evaporates, and the rest falls into the sump 24, and the water supply pump 22 circulates, and the high-temperature fluid is cooled to a low-temperature fluid and then flows out from the outlet header 29.
  • the present invention may also provide another type of evaporative condenser having a packing structure, including a coil heat exchanger, a fan 21, a water pump 22, a water distributor 23, a sump 24, and a frame 25;
  • the heat exchanger is composed of a plurality of serpentine coils formed by a plurality of serpentine coils connected by an inlet header 28 and an outlet header 29.
  • Each of the heat exchange fins includes a longitudinal serpentine (S-shaped) coil 26 and a packing 27, and the packing 27 is disposed between the adjacent heat exchange tubes 20 to form a gap coupling, that is, filling the heat exchange tubes 261 by the packing 27. The gap between them is to connect the coil 26 and the filler 27 into a continuous flow surface.
  • the above-mentioned filler 27 can be fixed between the coil 26 and the packing 27 by means of splicing, snapping or connecting means between the heat exchange tubes of the coil 26.
  • the connecting member is a tying rope F, and one or more fixing holes are formed at the edge of the packing 27, and a tying rope passes through the fixing hole and is firmly tied to the corresponding heat exchange tube 261.
  • the heat transfer tube of the coil is a circular tube or an elliptical tube, it is also possible to adopt a snapping manner, that is, the edge of the packing is set as a U-shaped groove to securely accommodate the heat exchange tube of the coil.
  • the packing disposed between adjacent heat exchange tubes may be one piece or a plurality of pieces.
  • the coil in this embodiment can also adopt other structures.
  • the straight pipe sections of the heat exchange tubes 26! of the coil 26 are parallel to each other, and the pipe pitch is gradually reduced from the upper layer to the lower layer. Accordingly, the radius of curvature of the curved portion of the heat exchange tube 261 is also gradually reduced, and the use of the filler 27 and the manner of connection with the coil 26 can be referred to the above embodiment.
  • the upper heat exchange tube 26 first receives the spray cold water, and then recognizes to flow down to the lower heat exchange tube 261; when the high temperature refrigerant enters from the inlet and then flows out from the outlet, due to the upper layer of the tube
  • the temperature of the refrigerant is higher than the temperature of the next layer, so the temperature of the water passing through the upper heat exchange tube 261 rises higher than the temperature of the water passing through the heat exchange tube 261 of the next layer, so the filler 27 of the upper layer is lengthened. It is used to extend the heat exchange time of the cooling water in the filler 27.
  • the coil of the structure can reduce the temperature difference between the lower heat exchange tube and the cooling water, thereby improving the heat exchange effect between the heat exchange tube and the cooling water, and is superior.
  • the coil shown in Fig. 15 and the straight tube of the heat exchange tube 261 of the coil has a downward slope along the direction of liquid flow within the tube, and the liquid in the tube is a high temperature refrigerant.
  • the high temperature refrigerant enters from the inlet, the flow of the refrigerant is in the downward slope direction until the outlet flows out. Since the heat exchange tube 261 has a certain downward slope along the direction of the flow, the coil more prominently reduces the pressure drop of the refrigerant from the mouth to the outlet.
  • FIG. 16 is a schematic cross-sectional view showing another condenser of the present invention for adding a heat exchange filler, between the serpentine coils 26 and the heat exchanger in the heat exchanger.
  • One or more pieces of filler 27' may be provided at the top or at the bottom of the heat exchanger.
  • Figures 17 and 18 show that the evaporative condenser places the fan 21 in the front of the heat exchanger (air inlet) and the wind turbine 2!
  • Figure! 9 shows that the evaporative condenser places the fan 21 vertically, and two sets of heat exchangers are disposed in the condenser.
  • Figure 20 also shows another implementation of an evaporative condenser having two sets of heat exchangers.
  • the heat exchange tubes of the heat exchanger used in this embodiment are not equal in length, that is, the length of the straight tube section of the heat exchange tube 261 of the coil is gradually increased from the upper layer to the next layer, wherein the upper heat exchange tube 261 first The sprayed cold water is received and then flows from top to bottom to the lower heat exchange tube 261.
  • the heat exchange fins provided in this embodiment are more suitable for evaporative condensers using two sets of heat exchangers. The difference from the embodiment shown in Fig.
  • this embodiment can install a fan of a larger size and horsepower by changing the length of the straight pipe section of the heat exchange pipe 261 without changing the outer dimensions of the condenser.
  • the fan 21 in the solid line portion is the heat exchange tube piece provided by the embodiment, and the fan 21' in the broken line portion is the heat exchange tube piece of the heat exchange tube having the straight pipe section of the equal length shown in Fig. 19.
  • the fan used in the former (solid line) is larger than the fan (dotted line) used in the latter, which increases the air volume and thus improves the heat transfer effect.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

Cet ensemble refroidisseur équipé d'un condenseur évaporatif (2) à serpentin de couplage avec matériau de remplissage comprend un compresseur (1), un condenseur évaporatif (2), un dispositif obturateur (3) et un évaporateur (4). Le condenseur évaporatif (2), comprenant un échangeur de chaleur, un système de ventilation (21), un distributeur (23) et un puisard (24), est constitué d'une pluralité de tuyaux à ailettes d'échangeur de chaleur connectés via un collecteur d'entrée (28) et un collecteur de sortie (29). Les tuyaux de l'échangeur thermique comprennent un serpentin (26) et un matériau de remplissage (27). Le serpentin (26) présente au moins un matériau de remplissage (27) destiné à acheminer l'eau de refroidissement vaporisée de la couche supérieure de l'échangeur de chaleur (261) vers la couche inférieure de l'échangeur de chaleur (261). Le serpentin (26) est placé en position verticale, ce qui permet au système de ventilation (21) de souffler sur le segment droit le long du serpentin (26) de l'air de refroidissement qui s'écoule sensiblement tout le long. L'invention a pour avantages de réduire la température de l'eau de refroidissement du serpentin (26) de refroidissement, d'augmenter le taux de couverture de distribution de l'eau de refroidissement circulant dans le serpentin (26) de refroidissement et de présenter une grande efficacité de transfert de chaleur.
PCT/CN2012/080018 2012-07-20 2012-08-13 Ensemble refroidisseur équipé d'un condenseur évaporatif à serpentin de couplage avec matériau de remplissage WO2014012286A1 (fr)

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CN110500817B (zh) * 2019-09-23 2024-03-22 广州市华德工业有限公司 一种播水换热装置以及制冷系统
CN117647150A (zh) * 2023-12-01 2024-03-05 山东贝诺冷却设备股份有限公司 低风阻填料模块和冷却塔

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