WO2017159515A1 - Dispositif et procédé d'évaluation d'échangeur de chaleur, procédé de fabrication d'échangeur de chaleur et procédé de conception d'échangeur de chaleur - Google Patents

Dispositif et procédé d'évaluation d'échangeur de chaleur, procédé de fabrication d'échangeur de chaleur et procédé de conception d'échangeur de chaleur Download PDF

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WO2017159515A1
WO2017159515A1 PCT/JP2017/009351 JP2017009351W WO2017159515A1 WO 2017159515 A1 WO2017159515 A1 WO 2017159515A1 JP 2017009351 W JP2017009351 W JP 2017009351W WO 2017159515 A1 WO2017159515 A1 WO 2017159515A1
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WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
refrigerant flow
flow path
heat exchange
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PCT/JP2017/009351
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English (en)
Japanese (ja)
Inventor
正也 倉地
峰正 大村
晋一 五十住
恵介 三苫
Original Assignee
三菱重工サーマルシステムズ株式会社
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Application filed by 三菱重工サーマルシステムズ株式会社 filed Critical 三菱重工サーマルシステムズ株式会社
Priority to EP17766516.3A priority Critical patent/EP3431904A4/fr
Priority to CN201780005295.3A priority patent/CN108474597A/zh
Publication of WO2017159515A1 publication Critical patent/WO2017159515A1/fr

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    • 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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F25B39/02—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

Definitions

  • the present invention relates to a heat exchanger evaluation apparatus, a heat exchanger evaluation method, a heat exchanger manufacturing method, and a heat exchanger design method.
  • a heat exchanger in which a plurality of mutually independent refrigerant flow paths are arranged in multiple stages in the vertical direction, and one end side of each of the plurality of refrigerant flow paths is connected to a refrigerant flow divider through a capillary tube.
  • Patent Document 1 when the heat exchanger functions as a condenser, in order to prevent liquid refrigerant from accumulating in the lowermost refrigerant flow path and excessively increasing the degree of supercooling, the lowermost refrigerant flow is disclosed. It is disclosed that the height from the lower end of the path to the upper end of the lowermost capillary tube is adjusted.
  • connection positions of the plurality of refrigerant flow paths and the capillary tubes connected thereto are positions at regular intervals in the entire area of the total height in the vertical direction of the heat exchanger. Therefore, the distance in the vertical direction between the connection position between the uppermost refrigerant flow path and the capillary tube and the connection position between the lowermost refrigerant flow path and the capillary tube is substantially the same as the overall height of the heat exchanger.
  • the difference between the pressure due to the self-weight of the liquid refrigerant from the connection position of the uppermost refrigerant flow path to the refrigerant flow divider and the pressure due to the self-weight of the liquid refrigerant from the connection position of the lowermost refrigerant flow path to the refrigerant flow divider is large.
  • the liquid refrigerant from the plurality of capillary tubes is merged and equalized by the refrigerant flow divider, and the equalized pressure increases, and accordingly, the liquid refrigerant is not easily discharged from the lowermost refrigerant flow path to the capillary tube. There was a problem of staying inside the road.
  • the present invention has been made in view of such circumstances, and is a heat exchanger evaluation apparatus and a heat exchanger evaluation method capable of preventing refrigerant retention in the refrigerant flow path in the heat exchanger as much as possible.
  • An object of the present invention is to provide a heat exchanger manufacturing method and a heat exchanger design method.
  • a refrigerant is circulated through a plurality of refrigerant flow paths arranged in multiple stages along a vertical direction, and a heat exchange section that exchanges heat between the refrigerant and air is circulated.
  • a refrigerant collecting pipe to which one end sides of the plurality of refrigerant flow paths are respectively connected, a plurality of refrigerant distribution pipes respectively connected to the other end sides of the plurality of refrigerant flow paths, and a plurality of the refrigerant distribution pipes.
  • a heat exchanger evaluation device including a refrigerant flow divider that merges at a merge position, the vertical height of the refrigerant flow path at the outlet of the heat exchange unit for each of the refrigerant flow paths, and the heat The first pressure loss of the refrigerant in the refrigerant flow path of the exchange part, the second pressure loss of the refrigerant in the refrigerant distribution pipe, and the vertical direction from the lower end of the heat exchange part to the refrigerant flow path in the lowest vertical direction Previous based on the relationship with height
  • An evaluation device for a heat exchanger comprising a determining means for determining whether or not the refrigerant is accumulated in the heat exchange unit.
  • the vertical height at the outlet of the heat exchange section of the plurality of refrigerant flow paths arranged in multiple stages along the vertical direction, and the refrigerant flow in the heat exchange section that exchanges heat between the air and the refrigerant Based on the relationship between the first pressure loss of the refrigerant in the passage, the second pressure loss of the refrigerant in the refrigerant distribution pipe, and the vertical height from the lower end of the heat exchange section to the refrigerant flow path in the lowest vertical direction arranged in multiple stages. Then, it is determined whether or not the refrigerant is staying in the heat exchange unit.
  • coolant in a heat exchange part can be determined easily by using the information of each place through which a refrigerant
  • the heat exchanger functions as a condenser and it is determined that the supercooled liquid is retained in the heat exchange part, the height of the refrigerant flow path in the heat exchange part, the pressure loss of the refrigerant in the heat exchange part, By adjusting the relationship between the pressure loss of the refrigerant in the refrigerant distribution pipe and the height of the lowermost refrigerant flow path, it is possible to eliminate stagnation in the heat exchange section and to prevent the condenser from degrading in condensing capacity. .
  • the determination means of the heat exchanger evaluation device is configured such that the vertical height at the outlet of the heat exchange unit is hi, the first pressure loss is Pri, and the second pressure loss is Pci.
  • the vertical height from the lower end of the heat exchange section to the lowest refrigerant flow path in the vertical direction is h bottom , the refrigerant density is ⁇ , and the gravitational acceleration is g, You may determine whether the said refrigerant
  • Judgment is made simply by making a decision based on the conditional expression.
  • the refrigerant is circulated through a plurality of refrigerant flow paths arranged in multiple stages along the vertical direction, and a heat exchange unit that exchanges heat between the refrigerant and air, and the gas-phase refrigerant circulates.
  • a refrigerant collecting pipe to which one end sides of the plurality of refrigerant flow paths are respectively connected, a plurality of refrigerant distribution pipes respectively connected to the other end sides of the plurality of refrigerant flow paths, and a plurality of the refrigerant distribution pipes.
  • An evaluation method of a heat exchanger comprising a refrigerant flow divider to be merged at a merge position, information on the vertical height of the refrigerant flow path at the outlet of the heat exchange part of the heat exchanger to be evaluated, A first step of acquiring a first pressure loss of the refrigerant in the refrigerant flow path of the heat exchange unit and a second pressure loss of the refrigerant in the refrigerant distribution pipe, and for each of the refrigerant flow paths, the heat Vertical direction of the refrigerant flow path in the exchange section Based on the relationship between the height, the first pressure loss, the second pressure loss, and the vertical height from the lower end of the heat exchanging portion to the refrigerant flow path in the lowest vertical direction, the heat exchanging portion It is the evaluation method of the heat exchanger which has a 2nd process which determines whether the refrigerant
  • the height in the vertical direction at the outlet of the heat exchange unit is hi
  • the first pressure loss is Pri
  • the second pressure loss is Pci
  • the vertical direction from the lower end of the heat exchange unit When the height in the vertical direction to the refrigerant flow path at the bottom in FIG. 5 is h bottom , the refrigerant density is ⁇ , and the gravitational acceleration is g, the refrigerant stays in the heat exchange section based on the following formula: It may be determined whether or not.
  • a refrigerant is circulated through a plurality of refrigerant flow paths arranged in multiple stages along the vertical direction, and a heat exchange part that exchanges heat between the refrigerant and air is circulated.
  • a refrigerant collecting pipe to which one end sides of the plurality of refrigerant flow paths are respectively connected, a plurality of refrigerant distribution pipes respectively connected to the other end sides of the plurality of refrigerant flow paths, and a plurality of the refrigerant distribution pipes.
  • a method of manufacturing a heat exchanger comprising a refrigerant flow divider that merges at a merge position, wherein for each of the refrigerant flow paths, the vertical height of the refrigerant flow path at the outlet of the heat exchange unit is hi,
  • the first pressure loss of the refrigerant in the refrigerant flow path of the heat exchange part is denoted as Pri
  • the second pressure loss of the refrigerant in the refrigerant distribution pipe is denoted as Pci
  • the lowermost refrigerant in the vertical direction from the lower end of the heat exchange part Vertical height to the flow path was a h bottom
  • the refrigerant density as a [rho, when the gravitational acceleration is g, a method of manufacturing a heat exchanger to produce said heat exchanger satisfying Equation below.
  • a refrigerant is circulated through a plurality of refrigerant flow paths arranged in multiple stages along a vertical direction, and a heat exchange part that exchanges heat between the refrigerant and air is circulated.
  • a refrigerant collecting pipe to which one end sides of the plurality of refrigerant flow paths are respectively connected, a plurality of refrigerant distribution pipes respectively connected to the other end sides of the plurality of refrigerant flow paths, and a plurality of the refrigerant distribution pipes.
  • the first pressure loss of the refrigerant in the refrigerant flow path of the heat exchange part is denoted as Pri
  • the second pressure loss of the refrigerant in the refrigerant distribution pipe is denoted as Pci
  • the present invention has an effect of preventing as much as possible refrigerant stagnation in the refrigerant flow path in the heat exchanger.
  • FIG. 1 shows a system configuration diagram of an evaluation system 3 of the present embodiment.
  • the evaluation system 3 includes a heat exchange system 1 and an evaluation device 30.
  • the evaluation apparatus 30 may use the outdoor heat exchanger (heat exchanger) 100 as an evaluation target or the indoor heat exchanger (heat exchanger) 200 as an evaluation target, but in the following description, A case where the outdoor heat exchanger 100 is an evaluation target will be described as an example.
  • the heat exchange system 1 is a system in which the outdoor heat exchanger 100 and the indoor heat exchanger 200 are connected by a refrigerant system to circulate the refrigerant.
  • An example of the heat exchange system 1 is an air conditioning system in which one or more indoor heat exchangers are connected to one outdoor heat exchanger.
  • Another example of the heat exchange system 1 is a heat pump hot water supply system using a CO 2 refrigerant.
  • the heat exchange system 1 includes an outdoor heat exchanger 100, an indoor heat exchanger 200, a compressor 210 that compresses a refrigerant, and a liquid component contained in a high-temperature and high-pressure refrigerant gas. It is the system
  • the heat exchanging system 1 shown in FIG. 1 can selectively execute a cooling operation for cooling the room and a heating operation for heating the room by switching the circulation direction of the refrigerant by the four-way valve 230.
  • the four-way valve 230 guides the refrigerant compressed by the compressor 210 to the indoor heat exchanger 200 to cause the indoor heat exchanger 200 to function as a condenser (condenser), and is adiabatically expanded by the expansion valve 240.
  • the direction of circulation of the refrigerant is set so as to guide the refrigerant to the outdoor heat exchanger 100 to function as an evaporator (evaporator) (direction indicated by a solid arrow in FIG. 1).
  • the four-way valve 230 guides the refrigerant compressed by the compressor 210 to the outdoor heat exchanger 100 so that the outdoor heat exchanger 100 functions as a condenser (condenser), and the expansion valve 240 insulates the air.
  • the circulation direction of the refrigerant is set so that the expanded refrigerant is guided to the indoor heat exchanger 200 to function as an evaporator (evaporator) (direction indicated by a broken arrow in FIG. 1).
  • the evaluation device 30 includes an acquisition unit 31 and a determination unit (determination unit) 32.
  • strain of the outdoor heat exchanger 100 from the side surface is shown by FIG.
  • the acquisition unit 31 includes the refrigerant flow paths 11, 12, 13, and 14 from the lower end of the heat exchange unit 10 at the outlet of the heat exchange unit 10 of the heat exchanger (outdoor heat exchanger or indoor heat exchanger) to be evaluated.
  • the second pressure loss of the refrigerant at 21 cbottom is acquired.
  • the determination unit 32 has a vertical height of the refrigerant flow channels 11, 12, 13, 14 from the lower end of the heat exchange unit 10 at the outlet of the heat exchange unit 10 with respect to the respective refrigerant flow channels 11, 12, 13, 14. Then, based on the relationship between the first pressure loss, the second pressure loss, and the vertical height from the lower end of the heat exchange unit 10 to the refrigerant flow path 14 in the lowest vertical direction, the refrigerant is accumulated in the heat exchange unit 10. It is determined whether or not. Specifically, the determination unit 32 sets the first pressure loss to Pri, the second pressure loss to Pci, and sets the height in the vertical direction from the lower end of the heat exchange unit 10 to the lowest refrigerant flow path 14 in the vertical direction to h bottom. When the refrigerant density is ⁇ and the gravitational acceleration is g, it is determined based on the following formula whether or not the refrigerant is retained in the heat exchange unit.
  • the outdoor heat exchanger 100 includes a heat exchange unit 10, a refrigerant distribution pipe 21, a refrigerant header (refrigerant collecting pipe) 40, and a distributor (refrigerant distributor) 50.
  • the heat exchange unit 10 circulates the refrigerant through a plurality of refrigerant flow paths (circuits) 11, 12, 13, and 14 arranged along the vertical direction, and is a blower fan (not shown) provided in the outdoor heat exchanger 100. The heat exchange with the air blown by is performed.
  • the refrigerant flow paths 11, 12, 13, and 14 are tube-shaped members formed of a metal member such as copper, and a flow path through which the refrigerant flows is formed.
  • the heat exchange unit 10 has the plurality of refrigerant flow paths 11, 12, 13, and 14 inserted into insertion holes of a plurality of aluminum plate-like fins (not shown) that are continuously arranged in the horizontal direction. It can be configured as a fin-and-tube heat exchanger.
  • the refrigerant header 40 is a pipe through which a gas-phase refrigerant flows and one end sides of the plurality of refrigerant flow paths 11, 12, 13, and 14 are connected at the first connection position C1.
  • the refrigerant header 40 supplies gas-phase refrigerant to the plurality of refrigerant flow paths 11, 12, 13, and 14.
  • the outdoor heat exchanger 100 functions as an evaporator (evaporator)
  • a gas-phase refrigerant is supplied to the refrigerant header 40 from the plurality of refrigerant flow paths 11, 12, 13, and 14.
  • the refrigerant distribution pipe 21 is configured by capillary tubes 21 c1 , 21 c2 , 21 ci ... 21 cbottom connected to the other end sides of the plurality of refrigerant flow paths 11, 12, 13, 14 at the second connection position C 2, respectively.
  • the distributor 50 is a device that joins the capillary tubes 21 c1 , 21 c2 , 21 ci ... 21 cbottom at the joining position C3.
  • the joining position C3 is arranged at a position below the lower end of the heat exchanging unit 10 in the vertical direction orthogonal to the installation surface of the outdoor heat exchanger 100 (that is, the vertical direction in FIG. 3).
  • the outdoor heat exchanger 100 When the outdoor heat exchanger 100 functions as a condenser (condenser), the supercooled liquid discharged from the second connection position C2 of the plurality of refrigerant flow paths 11, 12, 13, and 14 is capillary tubes 21 c1 , 21 c2 , 21 ci ... Is supplied to 21 cbottom and guided to the merge position C3 of the distributor 50.
  • the outdoor heat exchanger 100 when the outdoor heat exchanger 100 functions as an evaporator (evaporator), the supercooled liquid discharged from the junction position C3 of the distributor 50 is supplied to each of the capillary tubes 21 c1 , 21 c2 , 21 ci ... 21 cbottom . It is guided and supplied to the second connection position C2 of the plurality of refrigerant flow paths 11, 12, 13, and 14.
  • FIG. 3 is a diagram showing an example of a heat exchange model when the heat exchanger is used as a condenser.
  • the vertical direction in FIG. 3 coincides with the vertical direction based on the installation surface on which the outdoor heat exchanger 100 is installed.
  • the refrigerant flows from left to right on the paper surface of FIG.
  • the refrigerant passes through the refrigerant header 40 in a gas state, then passes through the heat exchanging unit 10 in a two-phase state, and finally passes through the capillary tubes 21 c1 , 21 c2 , 21 ci ... 21 cbottom in the liquid state,
  • the refrigerant in each refrigerant channel joins at the joining position C3.
  • each subscript represents the number of refrigerant flow paths (circuits), and “bottom” means the lowermost refrigerant flow path.
  • Pri is the pressure loss [Pa] in each refrigerant channel
  • Pci is the pressure loss [Pa] in each capillary tube
  • h is the height from the outlet of each refrigerant channel to the lower end of the heat exchanging unit 10 [ m]
  • h D is the height [m] from the lower end of the heat exchanger 10 to the lower end of the distributor 50
  • Pin is the inlet pressure [Pa]
  • Pout is the outlet pressure [Pa].
  • the refrigerant header 40 since the refrigerant state is gas, the density is small, and the position head pressure ⁇ gh is negligibly small compared to the pressure loss Pri of the refrigerant flow paths 11, 12, 13, 14 and the pressure loss Pci of the capillary tube. Further, when the refrigerant header 40 and the refrigerant flow paths 11, 12, 13, 14 are compared, the pipe length of the refrigerant header 40 is shorter than that of the refrigerant flow paths 11, 12, 13, 14 and the inner diameter of the refrigerant header 40 is greater than that of the refrigerant header 40. Since it is larger than the flow paths 11, 12, 13, and 14, the pressure loss in the refrigerant header 40 is so small that it can be ignored. Therefore, it can be assumed that the inlet pressure Pin in each refrigerant flow path 11, 12, 13, 14 is equal.
  • the outlet pressure Pout of each refrigerant flow path 11, 12, 13, 14 is designed to be equal, the outlet pressure Pout can also be assumed to be equal in each refrigerant flow path 11, 12, 13, 14.
  • the refrigerant density ⁇ is It can be assumed that 12, 13, and 14 are equal. From the assumptions described above, the relationship between the inlet pressure Pin and the outlet pressure Pout is expressed as in the following equations (1) to (2).
  • ⁇ is the refrigerant density [kg / m 3 ]
  • g is the gravitational acceleration [m / s 2 ].
  • the pressure loss is a function proportional to the square of the refrigerant flow path Gr [kg / h] as shown below.
  • ⁇ is the friction coefficient
  • L is the pipe length [m]
  • d is the pipe inner diameter [m]
  • A is the pipe cross-sectional area [m 2 ]
  • ⁇ L is the two-phase multiplication coefficient
  • x is the dryness.
  • FIG. 4 is a diagram illustrating an example of a heat exchange model when the heat exchanger is used as a condenser.
  • the distributor 50 is arranged at a position above the lower end of the heat exchanging unit 10 in the vertical direction orthogonal to the installation surface of the outdoor heat exchanger 100 (that is, the vertical direction in FIG. 4). Yes. Description of the parts having the same configuration as in FIG. 3 is omitted, and different parts are mainly described.
  • the liquid head of the refrigerant in the capillary tube 21 cbottom of the lowermost refrigerant flow path 14 will be considered.
  • the liquid head works so that the pressure is reduced.
  • the refrigerant once reaches a position higher than the upper end of the distributor 50, but then drops to the upper end of the distributor 50, so that the pressure is increased by h D ⁇ h bottom after all. Therefore, the relationship between the inlet pressure Pin and the outlet pressure Pout is expressed as follows.
  • equation (10) is equal to the above equation (3). Therefore, the same procedure as the process of deriving equation (6) is used. Substituting equation (10) into equation (4) yields equation (11) below, and equation (11) is exactly the same as equation (5).
  • equation (12) is obtained, and equation (12) is also the same as equation (6). If all the refrigerant flow paths 11, 12, and 13 satisfy the expression (12) (converted, the expression (13)), it is understood that no liquid pool is generated in the lowermost refrigerant flow path 14.
  • Equation (6) derived assuming that the distributor 50 is below the lower end of the heat exchange unit 10 is also derived from equation (12) derived assuming that the distributor 50 is above the lower end of the heat exchange unit 10.
  • h D indicating the height from the lower end of the heat exchange unit 10 to the upper end of the distributor 50 does not appear in the equation.
  • FIGS. 1-4 The height in the vertical direction from the lower end of the heat exchange section 10 of the refrigerant flow paths 11, 12, 13, and 14 at the outlet of the heat exchange section 10 of the heat exchanger to be evaluated is the heat exchanger that has already been manufactured.
  • the first pressure loss of the refrigerant in the refrigerant flow path of the heat exchange unit, and the second pressure loss of the refrigerant in the capillary tubes 21 c1 , 21 c2 , 21 ci ... 21 cbottom Based on the acquired information, it is determined whether or not the refrigerant is retained in the heat exchanging unit 10 depending on whether or not the above expression (7) (expression (13)) is established.
  • the capillary tubes 21 c1 , 21 c2 , 21 ci ... are changed by changing how the refrigerant flow paths 11, 12, 13 are assembled in the heat exchange unit 10 (that is, changing the circuit length of the heat exchange unit 10).
  • a countermeasure such as adjusting the length of 21 cbottom is conceivable.
  • the evaluation device 30 for the heat exchanger (the outdoor heat exchanger 100 and the indoor heat exchanger 200) according to the present embodiment, the heat exchanger evaluation method, the heat exchanger manufacturing method, and the heat exchange
  • the vertical heights h 1 , h 2 , h i of the outlets of the heat exchange unit 10 of the plurality of refrigerant flow paths 11, 12, 13 arranged in multiple stages along the vertical direction The first pressure loss of the refrigerant in the refrigerant flow paths 11, 12, 13, and 14 in the heat exchange unit 10 for exchanging heat between the air and the refrigerant, and the refrigerant first in the capillary tubes 21 c1 , 21 c2 , 21 ci ... 21 cbottom .
  • the refrigerant is retained in the heat exchanging unit 10. Determine whether.
  • coolant in the heat exchange part 10 can be determined easily by using the information of each place through which a refrigerant
  • the height of the refrigerant flow paths 11, 12, 13 of the heat exchange unit 10 and the heat exchange By adjusting the relationship between the pressure loss of the refrigerant in the section 10, the pressure loss of the refrigerant in the refrigerant distribution pipe (capillary tube) 21, and the height h cbottom of the lowermost refrigerant flow path 14, the residence in the heat exchange section It can be eliminated, and a reduction in the condensation capacity of the condenser can be prevented.
  • an evaluation device may be used at the stage of designing a heat exchanger. Specifically, the height hi of each refrigerant flow path 11, 12, 13, 14 derived in the design stage, the first pressure loss in each refrigerant flow path 11, 12, 13, 14 and the capillary tubes 21 c1 , 21 c2 , 21 ci ...
  • the height h 1 of the outlet of the heat exchanging section 10 of each of the refrigerant flow paths 11, 12, 13, 14 , H 2 , h i , h bottom , adjustment of circuit length, capillary tube 21 c1 , 21 c2 , 21 ci ... 21 cbottom can be selected again.
  • an evaluation device may be used at the stage of manufacturing the heat exchanger. Specifically, the height hi of each refrigerant flow path 11, 12, 13, 14 obtained in the manufacturing stage, the first pressure loss in each refrigerant flow path 11, 12, 13, 14 and the capillary tubes 21 c1 , 21 c2 , 21 ci ... The second pressure loss at 21 cbottom and the information of the height h cbottom of the refrigerant flow path 14 at the lowest stage from the heat exchanger 10 are substituted into the above equation (7), and the above equation (7) is established. If so, it is determined that there is no stagnation of the refrigerant, and the manufacturing process proceeds.
  • the heights h 1 , h 2 , h of the outlets of the heat exchanging portions 10 of the refrigerant flow paths 11, 12, 13, 14 are determined. Adjustment of i and h bottom , adjustment of circuit length, selection of capillary tubes 21 c1 , 21 c2 , 21 ci ... 21 cbottom , and manufacture a heat exchanger so that the above equation (7) is satisfied. can do.

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

Abstract

La présente invention a pour but d'empêcher, autant que possible, l'accumulation de fluide frigorigène dans un circuit d'écoulement de fluide frigorigène dans un échangeur de chaleur. Ainsi, l'invention concerne un dispositif d'évaluation destiné à un échangeur de chaleur comprenant : une unité d'échange de chaleur amenant un fluide frigorigène à circuler à travers une pluralité de circuits d'écoulement de fluide frigorigène à étages multiples agencés dans la direction verticale, et effectuant un échange de chaleur entre le fluide frigorigène et l'air ; un collecteur de fluide frigorigène à travers lequel circule un fluide frigorigène en phase gazeuse et auquel est relié un côté d'extrémité de chacun de la pluralité de circuits d'écoulement de fluide frigorigène ; une pluralité de tubes capillaires reliés aux autres côtés d'extrémité respectifs de la pluralité de circuits d'écoulement de fluide frigorigène ; et un distributeur reliant la pluralité de tubes capillaires au niveau d'une position de liaison. Le dispositif d'évaluation est muni d'une unité de détermination destinée à déterminer, pour chacun des circuits d'écoulement de fluide frigorigène, si le fluide frigorigène s'accumule dans l'unité d'échange de chaleur sur la base de la relation entre la hauteur verticale du circuit d'écoulement de fluide frigorigène au niveau d'une sortie de l'unité d'échange de chaleur, une première perte de pression (Pri) du fluide frigorigène dans le circuit d'écoulement de fluide frigorigène de l'unité d'échange de chaleur, une seconde perte de pression (Pci) du fluide frigorigène dans le tube capillaire correspondant, et une hauteur verticale (hi) de l'extrémité inférieure de l'unité d'échange de chaleur au circuit d'écoulement de fluide frigorigène le plus bas dans la direction verticale.
PCT/JP2017/009351 2016-03-15 2017-03-09 Dispositif et procédé d'évaluation d'échangeur de chaleur, procédé de fabrication d'échangeur de chaleur et procédé de conception d'échangeur de chaleur WO2017159515A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP17766516.3A EP3431904A4 (fr) 2016-03-15 2017-03-09 Dispositif et procédé d'évaluation d'échangeur de chaleur, procédé de fabrication d'échangeur de chaleur et procédé de conception d'échangeur de chaleur
CN201780005295.3A CN108474597A (zh) 2016-03-15 2017-03-09 热交换器的评价装置、热交换器的评价方法、热交换器的制造方法以及热交换器的设计方法

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Application Number Priority Date Filing Date Title
JP2016-050950 2016-03-15
JP2016050950A JP2017166728A (ja) 2016-03-15 2016-03-15 熱交換器の評価装置、熱交換器の評価方法、熱交換器の製造方法、並びに熱交換器の設計方法

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WO2017159515A1 true WO2017159515A1 (fr) 2017-09-21

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JP3985831B2 (ja) * 2005-10-31 2007-10-03 ダイキン工業株式会社 室外ユニット用熱交換器
JP2014025673A (ja) * 2012-07-30 2014-02-06 Fujitsu General Ltd 空気調和装置
WO2014080496A1 (fr) * 2012-11-22 2014-05-30 三菱電機株式会社 Climatiseur et procédé de commande de fonctionnement s'y rapportant
WO2014132650A1 (fr) * 2013-02-28 2014-09-04 Mitsubishi Electric Corporation Appareil de climatisation
JP2015214945A (ja) * 2014-05-13 2015-12-03 三菱電機株式会社 燃料供給装置

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Publication number Priority date Publication date Assignee Title
JP5790730B2 (ja) * 2012-12-25 2015-10-07 ダイキン工業株式会社 熱交換器

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Publication number Priority date Publication date Assignee Title
JP3985831B2 (ja) * 2005-10-31 2007-10-03 ダイキン工業株式会社 室外ユニット用熱交換器
JP2014025673A (ja) * 2012-07-30 2014-02-06 Fujitsu General Ltd 空気調和装置
WO2014080496A1 (fr) * 2012-11-22 2014-05-30 三菱電機株式会社 Climatiseur et procédé de commande de fonctionnement s'y rapportant
WO2014132650A1 (fr) * 2013-02-28 2014-09-04 Mitsubishi Electric Corporation Appareil de climatisation
JP2015214945A (ja) * 2014-05-13 2015-12-03 三菱電機株式会社 燃料供給装置

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See also references of EP3431904A4 *

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EP3431904A1 (fr) 2019-01-23
EP3431904A4 (fr) 2019-04-17
JP2017166728A (ja) 2017-09-21
CN108474597A (zh) 2018-08-31

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