WO2014068687A1 - Échangeur de chaleur à courants parallèles et climatiseur l'utilisant - Google Patents

Échangeur de chaleur à courants parallèles et climatiseur l'utilisant Download PDF

Info

Publication number
WO2014068687A1
WO2014068687A1 PCT/JP2012/078090 JP2012078090W WO2014068687A1 WO 2014068687 A1 WO2014068687 A1 WO 2014068687A1 JP 2012078090 W JP2012078090 W JP 2012078090W WO 2014068687 A1 WO2014068687 A1 WO 2014068687A1
Authority
WO
WIPO (PCT)
Prior art keywords
pipe
heat exchanger
header
header pipe
inflow
Prior art date
Application number
PCT/JP2012/078090
Other languages
English (en)
Japanese (ja)
Inventor
一樹 吉村
久保田　淳
石井　英二
Original Assignee
株式会社 日立製作所
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 株式会社 日立製作所 filed Critical 株式会社 日立製作所
Priority to JP2014544107A priority Critical patent/JP5957535B2/ja
Priority to PCT/JP2012/078090 priority patent/WO2014068687A1/fr
Publication of WO2014068687A1 publication Critical patent/WO2014068687A1/fr

Links

Images

Classifications

    • 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
    • F28D1/053—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 straight
    • F28D1/0535—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 straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • 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
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
    • 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
    • F28F9/0243—Header boxes having a circular cross-section
    • 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
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators
    • 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
    • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • F28D2021/0063—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
    • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • F28D2021/0064—Vaporizers, e.g. evaporators

Definitions

  • the present invention relates to a parallel flow heat exchanger and an air conditioner using the same.
  • a parallel flow type heat exchanger that has a plurality of flat tubes between two header tubes and performs heat exchange by refrigerant flow in the header and flat tubes is widely used in automobile radiators, air conditioners for cooling, etc. There is.
  • the refrigerant is a gas-liquid two-phase flow
  • the inside of the header pipe becomes a complicated flow field, and uniform distribution is difficult.
  • the pressure distribution is dispersed due to the flow colliding with the flat tube protruding into the header tube.
  • the height of the refrigerant gas-liquid interface fluctuates. Due to these phenomena, the refrigerant distribution amount to each flat tube is biased. As a result, the performance of the heat exchanger is degraded.
  • the parallel flow type heat exchanger includes the first header pipe and the second header pipe, the plurality of flat pipes connecting the first header pipe and the second header pipe, and the first header pipe, and the refrigerant flows therein.
  • the inflow pipe is arranged such that the central axis of the inflow pipe is offset with respect to the central axis of the first header pipe.
  • FIG. 2 is a diagram showing a parallel flow type heat exchanger in Embodiment 1.
  • FIG. 6 is a view showing a turning induction structure by an inflow pipe in the first embodiment.
  • FIG. 6 is a diagram showing a refrigerant flow field in a header pipe in Embodiment 1.
  • FIG. 7 is a three-dimensional view of a parallel flow heat exchanger in Embodiment 2.
  • FIG. 7 is a view showing a connection relationship between an inflow pipe and a header pipe in a second embodiment.
  • FIG. 7 is a view showing a connection relationship between an inflow pipe and a header pipe in a second embodiment.
  • FIG. 7 is a view showing a parallel flow type heat exchanger in a third embodiment.
  • FIG. 7 is a view showing a parallel flow type heat exchanger in a third embodiment.
  • FIG. 16 is a view showing a header pipe in a fourth embodiment.
  • FIG. 16 is a view showing a swirl flow guide plate in a fourth embodiment.
  • FIG. 18 is a diagram showing a parallel flow type heat exchanger in a fifth embodiment.
  • the parallel flow type heat exchanger includes a first header pipe and a second header pipe, a plurality of flat pipes connecting the first header pipe and the second header pipe, and a refrigerant connected to the first header pipe.
  • the inflow pipe is arranged such that the central axis of the inflow pipe is offset with respect to the central axis of the first header pipe, and the outflow pipe connected to the second header pipe and the outflow pipe through which the refrigerant flows out .
  • FIG. 14 is a diagram showing the configuration of a refrigeration cycle of a home air conditioner.
  • reference numeral 101 denotes a compressor
  • 102 denotes a four-way valve
  • 103 denotes an expansion device such as a motor operated valve
  • 104 denotes an outdoor heat exchanger
  • 106 denotes an indoor heat exchanger.
  • a cooling operation (solid arrow) using the outdoor heat exchanger 104 as an evaporator and the indoor heat exchanger 106 as a condenser, an outdoor heat exchanger 104 as a condenser, indoor heat A heating operation (broken line arrow) can be performed using the exchanger 106 as an evaporator.
  • the high-temperature and high-pressure refrigerant compressed by the compressor 101 passes through the four-way valve 102, flows into the outdoor heat exchanger 104, dissipates heat by heat exchange with air, and condenses.
  • the gas-liquid two-phase flow in which gas and liquid are mixed at low temperature and low pressure flows into the indoor heat exchanger 106.
  • the refrigerant absorbs heat from the air through the fins attached to the refrigerant pipe and the refrigerant pipe, and the refrigerant evaporates into a gas refrigerant from the inlet to the outlet. Then, the refrigerant that has exited the indoor heat exchanger 106 returns to the compressor 101 to form a cycle.
  • a piping structure in which one refrigerant pipe is branched into a plurality of refrigerant pipes is required.
  • FIG. 15 shows a configuration diagram of a refrigeration cycle in the case of adopting a reheat dehumidifying system in which the blowoff temperature of the indoor unit is not lowered.
  • the throttling device 105 is provided between the indoor heat exchangers 107 and 108, and the refrigerant is decompressed by the throttling device 105 so that the portion of the indoor heat exchanger 108 acts as a condenser and the portion of the indoor heat exchanger 107 acts as an evaporator. Then, the outlet temperatures of the indoor heat exchanger 107 and the indoor heat exchanger 108 are mixed.
  • a cross fin tube type heat exchanger is used for the outdoor heat exchanger 104 and the indoor heat exchangers 106, 107, 108.
  • a parallel flow type heat exchanger which is used in a radiator of a car, a dedicated air conditioner for cooling, etc., as a condenser and an evaporator. Therefore, it becomes an issue to distribute the refrigerant evenly from the header pipe of the parallel flow heat exchanger to the plurality of flat pipes.
  • FIG. 1 is a view showing the structure of a conventional parallel flow type heat exchanger.
  • the parallel flow type heat exchanger has header pipes 21 and 22 in which the refrigerant branches and joins at both ends of the flat pipes 11 arranged at equal intervals, and the header pipes 21 and 22 are inflow and outflow pipes 31 and 32 of the refrigerant. Have. Further, the inside of the flat tube 11 is divided by a thinner flow passage. Between the flat tubes 11, fins 4 for improving the efficiency of heat exchange are installed. For example, when the refrigerant flows in from the inflow pipe 31, the refrigerant is distributed to the flat pipes 11 in the header pipe 21. Then, after joining at the header pipe 22, it flows out from the outflow pipe 32. The same applies to the case where the inflow pipe is 32 and the outflow pipe is 31.
  • FIG. 2 is a view showing a parallel flow type heat exchanger of the present embodiment.
  • the basic configuration is the same as in FIG.
  • the heat exchanger comprises a flat pipe 12, header pipes 21 and 22, an outflow pipe 32 installed on the end face of the header pipe 22, an inflow pipe 33 installed on the side surface of the header pipe 21, and a fin installed between the flat pipes 12. It consists of four.
  • the structure for inducing the swirling flow in the header pipe 21 by the inflow pipe 33 will be described, but it is possible to induce the swirling flow also in the header pipe 22 with the same structure.
  • the positions of the header pipe 21 and the inflow pipe 33 and the details of the flat pipe 12 will be described with reference to FIG.
  • FIG. 3 is a view for explaining the positional relationship between the header pipe 21 and the inflow pipe 33 of FIG.
  • the inflow pipe 33 is installed such that the central axis 61 of the inflow pipe 33 and the longitudinal central axis 62 of the header pipe 21 are offset by a distance ⁇ with the side surface of the header pipe 21.
  • a swirling flow of refrigerant is induced in the pipe 21.
  • the liquid refrigerant is not biased toward the inflow pipe in the header pipe 21 or in the lower part of the header pipe 21, and the upper portion in the header pipe 21 (inflow pipe end Since the liquid refrigerant can be distributed in part (1), the refrigerant can be distributed evenly to the flat tube 12.
  • the liquid refrigerant is also distributed in the upper part of the header pipe 21 (inflow pipe end part), there is no need to deeply insert the inflow pipe end part into the header pipe 21 to the lower inside of the header pipe 21. Can also be reduced. Further, for example, as in the flat tube 12 shown in FIG.
  • the insertion length of the flat tube 12 into the header tube 21 is shortened to the processing limit at which the header tube 21 and the flat tube 12 can be joined. And the like.
  • FIG. 4 is a view showing a flow field in the header pipe 21 of FIG. 1 which is a conventional structure.
  • the heat exchanger is composed of the flat pipe 11, the header pipe 21, the inflow pipe 31, and the gas-liquid refrigerant 5, and the illustration of the fins is omitted.
  • the refrigerant flowing from the inflow pipe forms a laminar flow in which the upper part is a gas refrigerant and the lower part is a liquid refrigerant, and flows in the header pipe 21.
  • the flow velocity of the refrigerant is high in the vicinity of the inlet pipe inlet, and the refrigerant collides with the flat pipe 11 which is protruded into the header pipe 21 by the flow colliding. Therefore, the refrigerant easily flows into the flat tube 11 in the vicinity of the inflow tube 31 and the distribution amount is increased.
  • the liquid refrigerant flowing as a laminar flow is repelled by the wall end at the wall end face downstream of the header pipe 21, the flow stagnates, and the interface of the liquid refrigerant becomes high. For this reason, the refrigerant is likely to flow into the flat tube 11 in the vicinity of the end face of the wall.
  • the flat tube 11 located at the central portion of the header tube 21 has a lower interface compared to both ends of the header tube 21, the end face (inflow port) of the flat tube 11 is unlikely to contact the liquid refrigerant, The amount of inflow decreases relatively.
  • distribution of distribution amount will arise between the flat tubes 11. As shown in FIG.
  • FIG. 5 is a view showing a flow field in the header pipe 21 of FIG. 2 which is a structure of the present embodiment.
  • the heat exchanger is composed of the flat pipe 12, the header pipe 21, the inflow pipe 33, and the gas-liquid refrigerant 5, and the illustration of the fins is omitted.
  • the inflow pipe 33 is installed so that the swirling flow is induced in the header pipe 21, the liquid refrigerant is pulled by the swirling flow of the gas refrigerant so as to cover the entire wall surface of the header pipe 21. Liquid refrigerant flows.
  • the flat tube 12 not only shortens the insertion length into the inside of the header tube 21 but also has an end face shape along the arc shape of the header tube 21.
  • the flat tube does not disturb the swirling flow, and the pressure distribution in the header tube 21 becomes even. Furthermore, the liquid refrigerant forming a liquid film on the wall surface of the header pipe 21 easily flows into the flat pipe 12.
  • the swirling speed is attenuated. Therefore, the turning force can be adjusted by reducing the diameter of the inflow pipe 33 according to the length of the header pipe 21 so that the swirling flow can be maintained in the entire header pipe 21.
  • a pipe having a small diameter is used as the inflow pipe 33, a taper or an orifice is provided at the pipe outlet, and a restriction is provided at the outflow portion.
  • the direction of gravity is not limited, and even when the structure of the header pipe is upside down or when the longitudinal direction of the header pipe is the direction of gravity, the distribution variation reduction effect can be obtained by the swirling of the refrigerant.
  • the central axis of the inflow pipe is inclined in the longitudinal direction of the header pipe.
  • the inflow pipe insertion angle into the header pipe 21 is inclined by ⁇ 1 toward the downstream side of the header pipe 21.
  • FIG. 6 is a three-dimensional view of the parallel flow heat exchanger in the second embodiment.
  • the heat exchanger comprises the flat pipe 12, the header pipe 21 and the inflow pipe 34, and the illustration of the fins is omitted.
  • the outlet pipe 34 is inclined ⁇ 1 toward the inflow pipe 34 with respect to the header pipe 21 so that the outlet of the inflow pipe 34 faces the downstream side of the header pipe 21.
  • the longitudinal velocity of the refrigerant flow in the header pipe 21 becomes larger toward the downstream side of the header pipe 21, so that the sustained distance of the swirling flow becomes relatively longer, especially the refrigerant in the downstream of the header pipe 21 Distribution of each flat tube 12 is improved.
  • the heat exchanger of FIG. 7 comprises a flat pipe 12, a header pipe 21, an inflow pipe 34, a refrigerant 5, a central axis 61 of the inflow pipe 34, and a longitudinal central axis 62 of the header pipe 21; .
  • ⁇ 1 is inclined to the side vertical direction of the header pipe 21.
  • FIG. 8 shows an example of a heat exchanger in which the inflow pipe insertion angle to the header pipe 21 is inclined by ⁇ 2 in the flow direction of the flat pipe.
  • the heat exchanger of FIG. 8 is composed of the flat pipe 12, the header pipe 21, the inflow pipe 34, and the refrigerant 5, whereby the gas-liquid refrigerant flows more along the side wall surface of the header pipe 21 and the swirl flow efficiently. Can be induced.
  • FIG. 9 shows an example of a heat exchanger in which the number of inflow pipes 34 inserted into the header pipe 21 is plural.
  • the heat exchanger of FIG. 9 includes a flat pipe 12, header pipes 21 and 22, four inflow pipes 34, an outflow pipe 32, and fins 4.
  • the inflow pipe 34 is structured to induce a swirling flow in the header pipe 21 as described in the above embodiments.
  • four inflow pipes 34 are provided for the header pipe 21.
  • the swirling force decreases with a decrease in the flow rate of refrigerant per inflow tube, but this can be coped with by reducing the outlet tube diameter of inflow tube 34.
  • a pipe having a small diameter is used as the inflow pipe 34, a taper or an orifice is provided at the pipe outlet, and the like.
  • the inflow pipes 34 are installed at four locations in FIG. 9, the use of more inflow pipes 34 can further reduce the variation in refrigerant distribution.
  • the installation position of the inflow pipe 34 is not limited to the header pipe 21 at equal intervals, and can be installed at unequal intervals to adjust the inflow rate to each flat pipe 12.
  • the header pipe 21 may be divided into a plurality of sections, and the inflow pipe 21 of the present embodiment may be connected to each of the plurality of sections.
  • FIG. 10 shows an example of a heat exchanger in which the partition wall 7 is provided inside the header pipe 21 as compared with the heat exchanger of FIG.
  • the header pipe 21 is further divided into four small rooms.
  • the installation position of the partition wall 7 is not limited to the header pipe 21 at equal intervals, and can be installed at unequal intervals to adjust the inflow rate to each flat tube 12.
  • a fourth embodiment will be described using the drawings.
  • the configuration of the heat exchanger and the swirl inducing structure are the same as in the first and second embodiments, and therefore the description thereof is omitted.
  • a spiral flow guide plate 8 is disposed inside the header pipe 21.
  • FIG. 11 is a view showing a header pipe provided with a swirl flow guide plate 8 to maintain the swirl flow.
  • the swirling flow guide plate 8 serving as a swirling flow guide is inserted along the side wall surface in the header pipe 21.
  • the heat exchanger of FIG. 11 is comprised from the flat pipe 12, the header pipe 21, the inflow pipe 34, and the rotational flow guide plate 8, and illustration of a fin is abbreviate
  • FIG. 12 is a detailed structural view of the swirl flow guide plate 8 of FIG.
  • the swirl flow is induced inside the header pipe 21 by adopting the same configuration as each of the above embodiments.
  • the longer the length in the longitudinal direction of the header pipe 21 is, the more the refrigerant flows downstream in the header pipe 21, the more the header pipe wall and the refrigerant, or the shear force generated between the gas refrigerant and the liquid refrigerant.
  • the effect of reducing the distribution of refrigerant is reduced. Therefore, in the present embodiment, by disposing the spiral flow guide plate 8 inside the header pipe 21, the refrigerant is guided so as to turn the inner wall of the header pipe 21, so that the reduction of the turning force is suppressed. be able to. Further, by correcting the direction of the velocity vector by the swirling flow guide plate upstream of the header pipe 21, it is possible to suppress the phenomenon that the refrigerant flows directly into the flat tube 12 by the strong swirling flow immediately after the refrigerant flows.
  • FIG. 12 is a detailed structure of the swirling flow guide plate.
  • the radial thickness of the swirling flow guide plate 8 is further increased from the upstream side to the downstream side of the header pipe 21. That is, the spiral flow guide plate 8 is configured such that the width of the plate from the upstream to the downstream of the header pipe gradually increases to t 1 ⁇ t 2 ⁇ t 3 . Thereby, the direction of the velocity vector of the refrigerant flow can be corrected more forcibly in the swirling direction even in the downstream of the header pipe 21 where the swirling force is attenuated, and the effect of the swirling flow can be sustained longer.
  • the pressure loss can be optimized because the thickness of the plate is changed according to the flow as compared with the case where the thickness of the swirling flow guide plate 8 is uniformly thickened and the force is applied to the flow. it can. This makes it possible to further suppress the dispersion of refrigerant distribution.
  • the combination of the installation of the plurality of inflow pipes 34 and the installation of the dividing wall 7 described in the third embodiment is also effective for reducing the variation in distribution of the refrigerant.
  • FIG. 13 is a view showing a swing induction structure by the inflow pipe 35 disposed between the header pipes when the heat exchangers are arranged in two rows in the front and back.
  • the heat exchangers comprising the header pipe, the flat pipe, and the fins are arranged in two rows connected in the front and back, and when the refrigerant flows from the header pipe in the front row into the header pipe in the rear row,
  • the swirl induction structure shown in each of the above embodiments is provided (that is, the heat exchanger on the downstream side of the refrigerant flow is constituted by the parallel flow heat exchanger of each of the above embodiments).
  • the heat exchanger of FIG. 13 has flat tubes 12 and 13, header tubes 22 in the front row, header tubes 23 in the rear row, inflow tube (outflow tube) 35, central axis 61 of inflow tube 35, and longitudinal central axis of header tube 23. It consists of 62.
  • the parallel flow type heat exchangers of the above embodiments other parallel flow type heat exchangers (a plurality of header pipes 22 and a header pipe (not shown), a header pipe 22 and a header pipe ( A plurality of flat pipes 12 connecting the not shown, an inflow pipe (not shown) connected to the header pipe (not shown) into which the refrigerant flows, and an outflow pipe 35 connected to the header pipe 22 and the refrigerant flows out And a parallel flow heat exchanger) are connected.
  • the outflow pipe 35 of another parallel flow heat exchanger is connected to the inflow pipe 35 of the parallel flow heat exchanger of each of the above embodiments, and the outflow pipe 35 of another parallel flow heat exchanger.
  • the refrigerant which has flowed out of the refrigerant flows into the header pipe 23 through the inflow pipe 35 of the parallel flow heat exchanger of each of the above embodiments.
  • the heat exchangers are arranged in two rows, for example, when the header pipe is installed separately in the vertical direction with respect to the direction of gravity, when the refrigerant flows from the header pipe at the top of the front row to the header pipe at the top of the rear row
  • the liquid refrigerant stagnates in the header tubes of the rear row, and the liquid refrigerant is less likely to be distributed to the flat tubes. Therefore, in the present invention, as shown in FIG. 13, the heat exchangers described in the above embodiments are applied to induce a swirling flow in the header pipe 23 at the upper part of the rear row, whereby the refrigerant is applied to each flat pipe 13. Distribute evenly.
  • the refrigerant flow field of this embodiment and the effect thereof will be described.
  • the refrigerant 5 having flowed into the front row is distributed to the flat tubes 12, and then flows through the flat tubes 12 and merges at the header tube 22.
  • the refrigerant 5 flows from the header pipe 22 through the inflow pipe (outflow pipe) 35 to the header pipe 23 installed in the heat exchanger in the rear row.
  • a swirling flow is induced in the same manner as in the above embodiments. Since the gas-liquid refrigerant is in a swirling flow, the liquid refrigerant does not stay in the header pipe 23. Therefore, the pressure distribution in the header pipe 23 becomes more uniform, and the refrigerant distribution variation to the flat pipe 13 is improved. Since the end surface shape of the flat tube 13 is along the header tube (the end surface shape of the flat tube 13 is a concave shape), the stagnation of the refrigerant can be further suppressed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'objet de la présente invention est de fournir un échangeur de chaleur à courants parallèles qui, avec une structure simple, induit un écoulement tourbillonnaire à l'intérieur d'un tube de collecteur et distribue le fluide frigorigène de manière homogène à tubes plats. Le présent échangeur de chaleur à courants parallèles comporte : des premier et second tubes de collecteur ; une pluralité de tubes plats reliés aux premier et second tubes de collecteur ; un tube d'entrée qui est relié au premier tube de collecteur et dans lequel s'écoule le fluide frigorigène ; et un tube de sortie qui est relié au second tube de collecteur et hors duquel s'écoule le fluide frigorigène. Le tube d'entrée est disposé de telle sorte que l'axe central du tube d'entrée est décalé par rapport à l'axe central du premier tube de collecteur.
PCT/JP2012/078090 2012-10-31 2012-10-31 Échangeur de chaleur à courants parallèles et climatiseur l'utilisant WO2014068687A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2014544107A JP5957535B2 (ja) 2012-10-31 2012-10-31 パラレルフロー型熱交換器及びこれを用いた空気調和気
PCT/JP2012/078090 WO2014068687A1 (fr) 2012-10-31 2012-10-31 Échangeur de chaleur à courants parallèles et climatiseur l'utilisant

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/078090 WO2014068687A1 (fr) 2012-10-31 2012-10-31 Échangeur de chaleur à courants parallèles et climatiseur l'utilisant

Publications (1)

Publication Number Publication Date
WO2014068687A1 true WO2014068687A1 (fr) 2014-05-08

Family

ID=50626657

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/078090 WO2014068687A1 (fr) 2012-10-31 2012-10-31 Échangeur de chaleur à courants parallèles et climatiseur l'utilisant

Country Status (2)

Country Link
JP (1) JP5957535B2 (fr)
WO (1) WO2014068687A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017154336A1 (fr) * 2016-03-10 2017-09-14 株式会社日立製作所 Échangeur de chaleur et pompe à chaleur utilisant celui-ci
WO2019026241A1 (fr) * 2017-08-03 2019-02-07 三菱電機株式会社 Distributeur de réfrigérant, échangeur thermique et dispositif à cycle de réfrigération
JP2019078419A (ja) * 2017-10-20 2019-05-23 株式会社デンソー 熱交換器
JP2019178804A (ja) * 2018-03-30 2019-10-17 ダイキン工業株式会社 熱交換器および空気調和装置
WO2021025151A1 (fr) * 2019-08-08 2021-02-11 株式会社デンソー Échangeur de chaleur
JPWO2021149222A1 (fr) * 2020-01-23 2021-07-29
US20220090864A1 (en) * 2019-09-11 2022-03-24 Carrier Corporation Heat exchanger assembly
US12025355B2 (en) 2020-01-23 2024-07-02 Mitsubishi Electric Corporation Outdoor unit of refrigeration cycle apparatus

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57196045A (en) * 1981-05-22 1982-12-01 Pirelli Header pipe for solar panel and its manufacture
JPH0228986U (fr) * 1988-08-12 1990-02-23
JPH04295599A (ja) * 1991-03-25 1992-10-20 Matsushita Refrig Co Ltd 熱交換器
JPH05223490A (ja) * 1992-02-13 1993-08-31 Matsushita Electric Ind Co Ltd 熱交換器
JP2002062062A (ja) * 2000-08-22 2002-02-28 Zexel Valeo Climate Control Corp 熱交換器
JP2005291624A (ja) * 2004-03-31 2005-10-20 Iwai Kikai Kogyo Co Ltd 多管式熱交換器
JP2006162339A (ja) * 2004-12-03 2006-06-22 Mitsubishi Heavy Ind Ltd 熱交換器及び原子炉
JP2012163313A (ja) * 2011-01-21 2012-08-30 Daikin Industries Ltd 熱交換器および空気調和機

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5246557A (en) * 1975-10-11 1977-04-13 Hitachi Ltd Hat exchanger
JP4176950B2 (ja) * 2000-11-02 2008-11-05 三菱電機株式会社 プレート熱交換器及びそれを備えた冷凍サイクルシステム
US7806171B2 (en) * 2004-11-12 2010-10-05 Carrier Corporation Parallel flow evaporator with spiral inlet manifold
JP4889011B2 (ja) * 2006-07-20 2012-02-29 株式会社Ｂ．Ｔ．Ｐ． 冷暖房空調システム
JP5385588B2 (ja) * 2008-10-30 2014-01-08 シャープ株式会社 空気調和機の室外機
JP2011185549A (ja) * 2010-03-09 2011-09-22 Fuji Electric Co Ltd 熱交換器

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57196045A (en) * 1981-05-22 1982-12-01 Pirelli Header pipe for solar panel and its manufacture
JPH0228986U (fr) * 1988-08-12 1990-02-23
JPH04295599A (ja) * 1991-03-25 1992-10-20 Matsushita Refrig Co Ltd 熱交換器
JPH05223490A (ja) * 1992-02-13 1993-08-31 Matsushita Electric Ind Co Ltd 熱交換器
JP2002062062A (ja) * 2000-08-22 2002-02-28 Zexel Valeo Climate Control Corp 熱交換器
JP2005291624A (ja) * 2004-03-31 2005-10-20 Iwai Kikai Kogyo Co Ltd 多管式熱交換器
JP2006162339A (ja) * 2004-12-03 2006-06-22 Mitsubishi Heavy Ind Ltd 熱交換器及び原子炉
JP2012163313A (ja) * 2011-01-21 2012-08-30 Daikin Industries Ltd 熱交換器および空気調和機

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017154336A1 (fr) * 2016-03-10 2017-09-14 株式会社日立製作所 Échangeur de chaleur et pompe à chaleur utilisant celui-ci
WO2019026241A1 (fr) * 2017-08-03 2019-02-07 三菱電機株式会社 Distributeur de réfrigérant, échangeur thermique et dispositif à cycle de réfrigération
JPWO2019026241A1 (ja) * 2017-08-03 2019-11-07 三菱電機株式会社 冷媒分配器、熱交換器及び冷凍サイクル装置
JP7010958B2 (ja) 2017-08-03 2022-01-26 三菱電機株式会社 冷媒分配器、熱交換器及び冷凍サイクル装置
JP2019078419A (ja) * 2017-10-20 2019-05-23 株式会社デンソー 熱交換器
JP2019178804A (ja) * 2018-03-30 2019-10-17 ダイキン工業株式会社 熱交換器および空気調和装置
WO2021025151A1 (fr) * 2019-08-08 2021-02-11 株式会社デンソー Échangeur de chaleur
US20220090864A1 (en) * 2019-09-11 2022-03-24 Carrier Corporation Heat exchanger assembly
JPWO2021149222A1 (fr) * 2020-01-23 2021-07-29
WO2021149222A1 (fr) * 2020-01-23 2021-07-29 三菱電機株式会社 Unité extérieure pour dispositif à cycle de réfrigération
JP7262625B2 (ja) 2020-01-23 2023-04-21 三菱電機株式会社 冷凍サイクル装置の室外機
US12025355B2 (en) 2020-01-23 2024-07-02 Mitsubishi Electric Corporation Outdoor unit of refrigeration cycle apparatus

Also Published As

Publication number Publication date
JP5957535B2 (ja) 2016-07-27
JPWO2014068687A1 (ja) 2016-09-08

Similar Documents

Publication Publication Date Title
WO2014068687A1 (fr) Échangeur de chaleur à courants parallèles et climatiseur l'utilisant
JP5071597B2 (ja) 熱交換器および空気調和機
US20180224220A1 (en) Stacking-type header, heat exchanger, and air-conditioning apparatus
US10168083B2 (en) Refrigeration system and heat exchanger thereof
WO2013160957A1 (fr) Échangeur de chaleur, unité intérieure, et dispositif de cycle de réfrigération
JP6104893B2 (ja) 熱交換器、冷凍サイクル装置、空気調和機及び熱交換方法
JP2012163328A5 (fr)
EP3051245B1 (fr) Collecteur de type stratifié, échangeur thermique, et appareil de climatisation
JP4659779B2 (ja) 熱交換器及びこの熱交換器を備えた空気調和機
JP2015049008A (ja) 空気調和機及び空気調和機用熱交換器
JP2015017738A (ja) 熱交換器
JP5951475B2 (ja) 空気調和装置及びそれに用いられる室外熱交換器
WO2015059832A1 (fr) Échangeur thermique et dispositif à cycle de réfrigération utilisant ledit échangeur thermique
EP2037186B1 (fr) Système de climatisation
WO2014155560A1 (fr) Échangeur de chaleur et conditionneur d'air à cycle de réfrigération l'utilisant
WO2017135442A1 (fr) Échangeur de chaleur
JP2016038115A (ja) 熱交換器
WO2016121119A1 (fr) Échangeur de chaleur et dispositif à cycle de réfrigération
EP3594591B1 (fr) Échangeur de chaleur et climatiseur
JP2003090691A (ja) フィンチューブ型熱交換器およびこれを用いた冷凍サイクル
JP6671380B2 (ja) 熱交換器
JP5864030B1 (ja) 熱交換器、及び、この熱交換器を備えた冷凍サイクル装置
JP6678413B2 (ja) 空気調和機
JP6230852B2 (ja) 空気調和機及び空気調和機用熱交換器
JP4874320B2 (ja) 熱交換器及びこの熱交換器を備えた空気調和機

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12887652

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2014544107

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12887652

Country of ref document: EP

Kind code of ref document: A1