WO2017130399A1 - Dispositif à cycle frigorifique et échangeur de chaleur à tubes plats - Google Patents

Dispositif à cycle frigorifique et échangeur de chaleur à tubes plats Download PDF

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Publication number
WO2017130399A1
WO2017130399A1 PCT/JP2016/052764 JP2016052764W WO2017130399A1 WO 2017130399 A1 WO2017130399 A1 WO 2017130399A1 JP 2016052764 W JP2016052764 W JP 2016052764W WO 2017130399 A1 WO2017130399 A1 WO 2017130399A1
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WO
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Prior art keywords
flat tube
cut
heat exchanger
virtual surface
parallel
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Application number
PCT/JP2016/052764
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English (en)
Japanese (ja)
Inventor
前田　剛志
裕樹 宇賀神
Original Assignee
三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2016/052764 priority Critical patent/WO2017130399A1/fr
Priority to JP2017563643A priority patent/JP6548749B2/ja
Publication of WO2017130399A1 publication Critical patent/WO2017130399A1/fr

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    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements

Definitions

  • the present invention relates to a refrigeration cycle apparatus and a flat tube heat exchanger, and more particularly to a structure for drainage properties such as condensed water.
  • the refrigeration cycle apparatus reduces the amount of refrigerant to be enclosed in order to suppress the global warming effect (reducing the refrigerant) and heat exchange of the heat exchanger to suppress an increase in power consumption. It is desirable to ensure performance.
  • the refrigerant capacity of the copper tube heat exchanger tends to be larger than the refrigerant capacity included in the entire refrigeration cycle apparatus. This is due to the fact that the structure of the copper circular tube heat exchanger is a circular tube.
  • a means for making the heat transfer tube a flat tube can be considered.
  • the flat tube has a smaller tube diameter than the circular tube and has a partition wall inside, so that the capacity of the refrigerant is smaller than that of the circular tube.
  • the flat tube has lower ventilation resistance than the circular tube. For this reason, when attaching a plurality of heat transfer tubes to the fin, the interval between the heat transfer tubes can be set small. That is, the heat transfer tubes can be mounted on the fins with high density, and the heat exchange performance can be improved.
  • flat tubes are less drainable than circular tubes. That is, since the flat tube has a horizontal portion unlike the circular tube, the dew condensation water generated when used as an evaporator tends to accumulate on the flat tube. If condensed water accumulates on the flat tube, it becomes frost between the fins and causes a reduction in heat exchange performance.
  • the dew condensation water on the top surface of the flat tube merges with the dew condensation water flowing from the upper portion of the flat tube, etc. of the fins, flows through the top surface of the flat tube by the action of gravity, and reaches the end of the flat tube It is to be guided.
  • the lower surface of the flat tube is a portion where the condensed water does not flow from the upper portion of the flat tube among the fins. That is, the lower surface of the flat tube is a portion where the flow of condensed water is less likely to occur than the upper surface of the flat tube. Therefore, even if the flat tube is inclined due to the action of surface tension, the dew condensation water on the lower surface of the flat tube is difficult to be guided to the end of the flat tube.
  • the present invention has been made to solve the above-described problems, and an object thereof is to provide a refrigeration cycle apparatus and a flat tube heat exchanger with improved drainage.
  • the refrigeration cycle apparatus is a refrigeration cycle apparatus including a heat exchanger and a blower that supplies air to the heat exchanger, and the heat exchanger is connected to the fins and the fins so that air flows in.
  • the first end located at the first end is connected to the first flat tube disposed below the second end located at the outflow of the air, and the fin, and is below the first flat tube.
  • a second flat tube disposed at an interval, the long axis of the first flat tube in a cross section parallel to the extending direction of the fins as the first long axis, and the second flat tube,
  • the major axis in the cross section parallel to the extending direction of the fin is the second major axis
  • the first major axis and the second major axis are parallel
  • the fin is composed of the first flat tube and the second flat axis.
  • a cut and raised piece is formed at a position between the tube and the cut and raised piece passes through the center between the first flat tube and the second flat tube
  • a plane parallel to the first major axis is defined as a first imaginary plane
  • a plane passing through the center of the width of the first major axis and the center of the width of the second major axis is defined as a second imaginary plane
  • a plane that is parallel to the long axis and passes through the lower surface of the first flat tube is defined as a third virtual plane
  • a surface that is parallel to the gravitational direction and passes through the first end of the first flat tube is defined as the fourth virtual surface.
  • the refrigeration cycle apparatus according to the present invention has the above-described configuration, the drainage of the heat exchanger can be further improved.
  • FIG. 1 It is a schematic block diagram which shows an example of the refrigerant circuit structure of the refrigerating-cycle apparatus which concerns on Embodiment 1 of this invention. It is a schematic block diagram of the flat tube heat exchanger of the refrigeration cycle apparatus which concerns on Embodiment 1 of this invention. It is sectional drawing of the flat tube heat exchanger of the refrigeration cycle apparatus which concerns on Embodiment 1 of this invention. It is a figure which shows the relationship between the amount of water remaining on the flat tube heat exchanger of the refrigerating-cycle apparatus which concerns on Embodiment 1 of this invention, and time.
  • FIG. 1A is a schematic configuration diagram illustrating an example of a refrigerant circuit configuration of a refrigeration cycle apparatus 100A according to Embodiment 1.
  • a refrigeration cycle apparatus 100A will be described based on FIG. 1A.
  • the refrigeration cycle apparatus 100 ⁇ / b> A includes an outdoor unit 1 and an indoor unit 2.
  • the outdoor unit 1 and the indoor unit 2 are connected via a liquid pipe 7 and a gas pipe 9 which are refrigerant pipes.
  • a refrigerant sealed in the refrigeration cycle apparatus 100A for example, a refrigerant having a property of self-decomposition can be used.
  • the outdoor unit (heat source unit) 1 includes a compressor 3 for compressing refrigerant, a four-way valve 4 as refrigerant circuit switching means for switching a refrigerant flow path, and air around the outdoor unit 1 conveyed by the refrigerant and the outdoor blower 5a. And an outdoor heat exchanger 5 for exchanging heat, and an electronic expansion valve 6 for controlling the flow rate of the refrigerant. Further, the outdoor heat exchanger 5 is provided with an outdoor fan 5 a that supplies air to the outdoor heat exchanger 5.
  • the indoor unit (use-side unit) 2 exchanges heat between the refrigerant and the air around the indoor unit 2 conveyed by the indoor blower 8a, and cools or heats the indoor space by, for example, cooling or heating the indoor space.
  • a heat exchanger 8 is provided.
  • the indoor heat exchanger 8 is provided with an indoor blower 8 a that supplies air to the indoor heat exchanger 8.
  • the compressor 3 for compressing the refrigerant it is preferable to use a positive displacement compressor of a type in which the rotation speed is controlled by an inverter circuit and the capacity is controlled.
  • the positive displacement compressor include a rotary compressor, a scroll compressor, a screw compressor, and a reciprocating compressor.
  • the compressor 3 is provided with an electric motor.
  • the four-way valve 4 switches the refrigerant flow path according to a cooling / heating supply mode (for example, cooling operation mode) and a heating / heating supply mode (for example, heating operation mode).
  • a cooling / heating supply mode for example, cooling operation mode
  • a heating / heating supply mode for example, heating operation mode
  • the refrigerant circuit switching unit may be configured by combining two refrigerant valves, for example, two two-way valves or three-way valves. Good.
  • the case where the four-way valve 4 is provided is shown as an example, when the refrigerant circuit configuration in which the refrigerant flow path is not switched is adopted as the refrigeration cycle apparatus 100A, it is not necessary to provide the refrigerant circuit switching means.
  • the outdoor heat exchanger 5 and the indoor heat exchanger 8 function as a condenser or an evaporator, and are configured by, for example, a cross-fin type fin-and-tube heat exchanger configured by heat transfer tubes and a large number of fins. be able to.
  • the outdoor blower 5a supplies air to the outdoor heat exchanger 5, and is configured to be capable of changing the air flow rate.
  • a centrifugal fan or a multiblade fan driven by a motor such as a DC fan motor can be used as the outdoor fan 5a.
  • a transport device such as a pump may be provided instead of the outdoor blower 5a.
  • the electronic expansion valve 6 can adjust the refrigerant flow rate.
  • the pressure reducing mechanism the electronic expansion valve 6 having a variable throttle opening is described as an example, but the present invention is not limited to this.
  • the pressure reducing mechanism may be configured by a mechanical expansion valve that employs a diaphragm for the pressure receiving portion, or a capillary tube.
  • the indoor blower 8a supplies air to the indoor heat exchanger 8, and is configured to be capable of changing the air flow rate.
  • a centrifugal fan or a multiblade fan driven by a motor such as a DC fan motor can be used as the indoor fan 8a.
  • a transfer device such as a pump may be provided instead of the indoor blower 8a.
  • the outdoor unit 1 and the indoor unit 2 comprise a refrigerant circuit by connecting each element apparatus with the liquid pipe 7 and the gas pipe 9 which are refrigerant flow paths.
  • the connection algebra of the outdoor unit 1 and the indoor unit 2 is not limited to one, and any one or each may be a plurality.
  • the refrigeration cycle apparatus 100A includes a control device 50 that performs overall control of the refrigeration cycle apparatus 100A.
  • the control device 50 controls each actuator (driving components such as the compressor 3, the four-way valve 4, the outdoor blower 5a, the electronic expansion valve 6, and the indoor blower 8a) based on the detection value from each detector.
  • the control device 50 can be configured by hardware such as a circuit device that realizes the function, or can be configured by an arithmetic device such as a microcomputer or a CPU and software executed thereon.
  • the four-way valve 4 in the cold supply mode (for example, cooling operation) in which cold is supplied from the indoor heat exchanger 8, the four-way valve 4 is a solid flow path, and a hot supply mode (for example, supplying warm heat from the indoor heat exchanger 8) (for example, In the heating operation), the four-way valve 4 is switched to a dotted flow path. Therefore, in the cold heat supply mode, the compressor 3, the four-way valve 4, the outdoor heat exchanger 5, the electronic expansion valve 6, the indoor heat exchanger 8, and the compressor 3 are connected in an annular shape in this order. In the heat supply mode, the compressor 3, the four-way valve 4, the indoor heat exchanger 8, the electronic expansion valve 6, the outdoor heat exchanger 5, and the compressor 3 are annularly connected in this order.
  • the outdoor heat exchanger 5 functions as a condenser
  • the indoor heat exchanger 8 functions as an evaporator.
  • the outdoor heat exchanger 5 functions as an evaporator
  • the indoor heat exchanger 8 functions as a condenser.
  • the outdoor heat exchanger 5 is described as an example of the flat tube heat exchanger 100 as an example, but the indoor heat exchanger 8 may be used.
  • FIG. 1B is a schematic configuration diagram of the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to the first embodiment.
  • FIG. 2 is a cross-sectional view of the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to the first embodiment.
  • FIG. 1B (a) shows a state in which a plurality of fins 30 are attached to the heat transfer tube 10.
  • FIG. 1B (b) is an explanatory diagram of the heat transfer tube 10. Note that the X direction, the Y direction, and the Z direction in FIG. 1B are orthogonal to each other.
  • FIG. 2 is a cross-sectional view in a cross section parallel to the extending direction of the fin 30. With reference to FIG. 1B and FIG. 2, the structure, function, etc. of the flat tube heat exchanger 100 are demonstrated.
  • the flat tube heat exchanger 100 includes a plate-like fin 30 and a heat transfer tube 10 provided so as to intersect the fin 30.
  • the heat transfer tube 10 is connected to the fins 30.
  • the heat transfer tube 10 includes a first flat tube 10A1, a second flat tube 10A2 provided to face the first flat tube 10A1, a first flat tube 10A1, and a second flat tube 10A2.
  • a curved portion 10B for connecting the two.
  • the heat transfer tube 10 shown in FIG. 1B (b) is connected to, for example, a header (not shown).
  • a plurality of flow paths F through which the refrigerant flows are formed in the first flat tube 10A1, the second flat tube 10A2, and the curved portion 10B.
  • the flat tube heat exchanger 100 is provided with a plurality of fins 30.
  • the plurality of fins 30 are arranged in the Y direction at regular intervals.
  • the plurality of fins 30 are provided in parallel with the Z direction. Further, the drain 30 is formed in the fin 30 to guide the condensed water downward.
  • the heat transfer tube 10 is formed with a flow path through which a refrigerant flows.
  • the first flat tube 10A1 and the second flat tube 10A2 are straight flat tubes.
  • the first flat tube 10 ⁇ / b> A ⁇ b> 1 is provided so as to intersect with the fins 30.
  • the second flat tube 10A2 is also provided so as to intersect the fins 30.
  • the first flat tube 10A1 is connected to the fins 30 and the second flat tube 10A2 is also connected to the fins 30.
  • the first flat tube 10A1 and the second flat tube 10A2 and the fins 30 are orthogonal to each other.
  • a gap is provided between the first flat tube 10A1 and the second flat tube 10A2.
  • the first flat tube 10A1 and the second flat tube 10A2 are arranged in parallel. That is, the long axis AX1 of the first flat tube 10A1 and the long axis AX2 of the second flat tube 10A2 are parallel.
  • the long axis AX1 is a long axis in a cross section of the first flat tube 10A1 parallel to the extending direction of the fins 30.
  • the long axis AX1 corresponds to the first long axis.
  • the long axis AX2 is a long axis in a cross section of the second flat tube 10A2 parallel to the extending direction of the fins 30.
  • the long axis AX2 corresponds to the second long axis.
  • the long axis AX1 is an axis in a cross section parallel to the fins 30 in the first flat tube 10A1, and is not an axis in a direction parallel to the flow path F.
  • the long axis AX2 is also an axis in a cross section parallel to the fins 30 in the second flat tube 10A2, and is not an axis in a direction parallel to the flow path F.
  • the shapes of the first flat tube 10A1 and the second flat tube 10A2 are the same.
  • the first flat tube 10A1 includes a first end E1 located at the end 13A of the drainage channel 13 and a second end E2 located farther from the drainage channel 13 than the first end E1. Including.
  • the first end E1 is located upstream of the second end E2 in the air flow direction. Further, in a state where the flat tube heat exchanger 100 is installed in the refrigeration cycle apparatus 100A, the first flat tube 10A1 is positioned above the second flat tube 10A2.
  • the 2nd flat tube 10A2 is also the structure according to 1st flat tube 10A1. That is, the second flat tube 10A2 includes a third end E3 located at the end 13A of the drainage channel 13 and a fourth end E4 located farther from the drainage channel 13 than the third end E3. Including.
  • the fin 30 is a plate-shaped member. A gap through which air flows is formed between adjacent fins 30.
  • the fin 30 has a plurality of notches into which the heat transfer tubes 10 are inserted. Specifically, the first flat tube 10A1 and the second flat tube 10A2 of the heat transfer tube 10 are inserted into each notch of the fin 30.
  • this Embodiment 1 demonstrates the aspect in which the notch is formed in the fin 30, it is an aspect in which the hole into which the 1st flat tube 10A1 and 2nd flat tube 10A2 are inserted was formed. Also good.
  • the fin 30 includes a drainage channel 13 formed so as to extend in parallel to a predetermined direction (X direction) from the first flat tube 10A1 toward the second flat tube 10A2.
  • the drainage channel 13 is located at the end of the fin 30 in the longitudinal direction.
  • the fin 30 includes a cut and raised piece 11 and a heat exchange cut and raised piece 12 formed at a position between the first flat tube 10A1 and the second flat tube 10A2.
  • the cut and raised pieces 11 and the heat exchange cut and raised pieces 12 have different main functions.
  • the cut and raised piece 11 mainly has a function of promptly guiding the condensed water adhering to the lower surface SF2 of the first flat tube 10A1 to the drainage channel 13. Specifically, condensed water adheres to the lower surface SF2 of the first flat tube 10A1 due to surface tension or the like.
  • the condensed water from the fins 30 is less likely to flow into the lower surface SF2 of the first flat tube 10A1. For this reason, the dew condensation water on the lower surface SF2 tends to remain attached to the lower surface SF2.
  • the cut-and-raised piece 11 is formed, (1) the condensed water on the lower surface SF2 is drawn into the cut-and-raised piece 11, and (2) the condensed water drawn into the cut-and-raised piece 11 is then discharged into the drainage channel 13. Flows in.
  • the cut and raised piece 11 has a function of promptly flowing the condensed water on the lower surface SF2 of the first flat tube 10A1 to the drainage channel 13 in particular.
  • the cut and raised pieces 12 for heat exchange are formed separately from the cut and raised pieces 11. That is, the cut and raised pieces 11 and the heat exchange cut and raised pieces 12 are not integrally but cut and raised pieces.
  • the heat exchange cut and raised piece 12 mainly has a function of improving the heat exchange performance of the flat tube heat exchanger 100.
  • the heat exchange cut and raised piece 12 is positioned above the upper surface SF3 of the second flat tube 10A2.
  • the condensed water adhering to the upper surface SF3 of the second flat tube 10A2 flows more quickly than the condensed water adhering to the lower surface SF4 of the second flat tube 10A2. This is because condensed water flows into the upper surface SF3 from the fins 30 and the like.
  • the cut and raised pieces 12 for heat exchange may be formed larger than the cut and raised pieces 11. If the cut-and-raised piece 11 is made too large, the surface tension of the condensed water drawn into the cut-and-raised piece 11 due to the action of (1) described above increases, and the action of (2) may be hindered. Because there is. That is, the condensed water drawn into the cut and raised pieces 11 is less likely to flow into the drainage channel 13. On the other hand, the cut and raised pieces 12 for heat exchange do not have such drainage as a main function. For this reason, the cut and raised pieces 12 for heat exchange may be larger than the cut and raised pieces 11. Thereby, the heat exchange performance of the fin 30 can be improved.
  • the first virtual plane PL1 is a plane that passes through the center between the first flat tube 10A1 and the second flat tube 10A2 and is parallel to the long axis AX1 of the first flat tube 10A1.
  • the second virtual plane PL2 is a plane that passes through the center of the width of the first flat tube 10A1 on the long axis AX1 and the center of the width of the second flat tube 10A2 on the long axis AX2.
  • the third virtual plane PL3 is parallel to the long axis AX1 of the first flat tube 10A1, and passes through the surface (upper surface SF3) facing the second flat tube 10A2 among the surfaces of the first flat tube 10A1. It is.
  • the fourth virtual plane PL4 is a plane that is parallel to the X direction and passes through the first end E1 of the first flat tube 10A1.
  • the fifth virtual surface PL5 is parallel to the long axis AX2 of the second flat tube 10A2 and passes through the surface (the lower surface SF2) facing the first flat tube 10A1 among the surfaces of the second flat tube 10A2.
  • the sixth virtual plane PL6 is a plane that is parallel to the X direction and passes through the third end E3 of the second flat tube 10A2. In the first embodiment, the fourth virtual surface PL4 and the sixth virtual surface PL6 are located on the same surface.
  • the cut-and-raised piece 11 is disposed in the first region RE1 defined by the first virtual surface PL1, the second virtual surface PL2, the third virtual surface PL3, and the fourth virtual surface PL4. More specifically, the cut-and-raised piece 11 is disposed at a position near the drainage channel 13 and near the lower surface SF2 in the first region RE1.
  • the heat exchange cut-and-raised piece 12 is disposed in the second region RE2 defined by the first virtual surface PL1, the second virtual surface PL2, the fifth virtual surface PL5, and the sixth virtual surface PL6. . More specifically, the heat exchange cut-and-raised piece 12 is disposed at a position near the drainage channel 13 and near the upper surface SF3 in the second region RE2.
  • the cut and raised pieces 11 and the heat exchange cut and raised pieces 12 are arranged in the first region RE1 and the second region RE2 of the fins 30, respectively.
  • the seventh virtual plane PL7 is a plane parallel to the X direction and passing through the second end E2 of the first flat tube 10A1.
  • the eighth virtual plane PL8 is a plane parallel to the X direction and passing through the fourth end E4 of the second flat tube 10A2.
  • the seventh virtual plane PL7 and the eighth virtual plane PL8 are located on the same plane.
  • a portion defined by the first virtual surface PL1, the second virtual surface PL2, the third virtual surface PL3, and the seventh virtual surface PL7 is referred to as a third region RE3.
  • a portion defined by the first virtual surface PL1, the second virtual surface PL2, the fifth virtual surface PL5, and the eighth virtual surface PL8 is referred to as a fourth region RE4.
  • the third region RE3 and the fourth region RE4 are both flat, and no cut and raised pieces are formed. By forming the cut and raised pieces, the pressure loss of the air passing through the fins 30 is prevented from increasing.
  • FIG. 3 is a diagram showing the relationship between the amount of water remaining on the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to Embodiment 1 and time.
  • the flat tube heat exchanger 100 functions as an evaporator
  • the condensed water generated on the lower surface SF2 of the first flat tube 10A1 is cut and raised by forming (standing) the cut pieces 11 on the surface of the fin 30.
  • Capillary force drawn into the piece 11 works. This makes it easy to reduce the amount M of dew condensation water adhering to the flat tube heat exchanger 100, and drains dew condensation water faster than the flat tube heat exchanger in which the fins 30 have no cut and raised pieces 11 on the surface. Can do.
  • the graph shown with the continuous line of FIG. 3 has shown the mode of the reduction
  • FIG. The broken line in FIG. 3 shows how the amount of water M decreases in the flat tube heat exchanger in the form in which the fin 30 is not cut and raised at all.
  • the dashed line in FIG. 3 shows how the amount of water M is reduced in the aspect of the flat tube heat exchanger in which the cut and raised pieces 11 and the heat raised and raised pieces 12 are integrally formed on the fin 30.
  • the amount of water M of the flat tube heat exchanger in which the cut and raised pieces 11 and the heat raised and raised pieces 12 are integrally formed on the fin 30 is also difficult to reduce.
  • the cut and raised pieces 11 and the heat exchange cut and raised pieces 12 are formed separately. That is, they are not united. As a result, the amount of condensed water held by the cut and raised piece alone is reduced, and the surface tension in the cut and raised piece is weakened. Therefore, the condensed water held by the cut and raised pieces 11 can be promptly guided to the drainage channel 13. As a result, the amount of water M remaining in the flat tube heat exchanger 100 can be easily reduced.
  • FIG. 4 is a diagram showing an improvement rate of the heat transfer performance ⁇ o by forming the cut and raised pieces 11 and the heat raised and raised pieces 12 in the flat tube heat exchanger of the refrigeration cycle apparatus 100A according to the first embodiment. is there.
  • the flat tube heat exchanger 100 functions as a condenser, the flow on the surface of the fin 30 is locally disturbed by forming the cut and raised pieces 11 and the cut and raised pieces 12 for heat exchange, and the air and the flat tube heat Since the heat exchange amount of the exchanger 100 is improved, the heat transfer performance ⁇ o is improved.
  • the flat tube heat exchanger 100 has a heat transfer performance ⁇ o improved by about 15% compared to a flat tube heat exchanger in which the cut and raised pieces 11 and the heat raised and raised pieces 12 are not formed. You can see that
  • FIG. 5 shows the improvement rate of year-round energy consumption efficiency (AFP) by forming the cut and raised pieces 11 and the heat raised and raised pieces 12 in the flat tube heat exchanger of the refrigeration cycle apparatus 100A according to the first embodiment.
  • AFP year-round energy consumption efficiency
  • the flat tube heat exchanger 100 has a year-round energy consumption efficiency of 0.5% compared to a flat tube heat exchanger in which the cut and raised pieces 11 and the heat raised and raised pieces 12 are not formed. It turns out that it has improved so much.
  • the heat transfer performance of the flat tube heat exchanger 100 is improved. Improvements can be made.
  • FIG. FIG. 6 is a cross-sectional view of the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to the second embodiment.
  • FIG. 6 is a cross-sectional view in a cross section parallel to the extending direction of the fin 30.
  • components that are the same as those in the first embodiment will be described with the same reference numerals, and different parts from the first embodiment will be mainly described.
  • the cut-and-raised piece 11 described in the first embodiment is formed to extend in parallel to the direction (X direction) from the first flat tube 10A1 toward the second flat tube 10A2.
  • the cut-and-raised piece 11B described in the second embodiment is formed so as to approach the drainage channel 13 from the portion near the first flat tube 10A1 toward the portion near the second flat tube 10A2. That is, the cut-and-raised pieces 11B are formed so as to cross rather than be parallel to the direction of gravity when the flat tube heat exchanger 100 is mounted on the refrigeration cycle apparatus 100A.
  • FIG. 7 is a diagram showing the relationship between the amount of water remaining on the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to Embodiment 2 of the present invention and time.
  • the cut-and-raised piece 11B has a configuration in which one end portion is disposed near the lower surface SF2 and the other end portion is disposed near the drainage channel 13. For this reason, the dew condensation water on the lower surface SF2 of the first flat tube 10A1 can be more reliably guided to the drainage channel 13.
  • the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100 ⁇ / b> A according to the second embodiment has a water amount M that is faster than the aspect of the first embodiment (see the broken line in FIG. 7). It turns out that it decreases.
  • FIG. 8 is a diagram showing the improvement rate of the heat transfer performance ⁇ o by forming the cut and raised pieces 11B and the heat raised and raised pieces 12 in the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to the second embodiment. It is. By forming the cut-and-raised piece 11B, the flow on the surface of the fin 30 is more locally disturbed than in the first embodiment, and the amount of heat exchange between the air and the flat tube heat exchanger 100 is improved. For this reason, the heat transfer performance ⁇ o is further improved as compared with the first embodiment. As shown in FIG. 8, it can be seen that the flat tube heat exchanger 100 of the second embodiment has improved the heat transfer performance ⁇ o by about 2.5% as compared with the aspect of the first embodiment.
  • FIG. 9 is a diagram showing a year-round energy consumption efficiency improvement rate by forming the cut and raised pieces 11B and the heat raised and raised pieces 12 in the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to the second embodiment. It is. By forming the cut-and-raised piece 11B, the ventilation resistance generated when air passes through the flat tube heat exchanger 100 is also increased. However, considering the energy consumption efficiency throughout the year, the energy consumption efficiency is improved because the contribution of the effect of improving the heat transfer performance is significant. As shown in FIG. 9, it can be seen that the flat tube heat exchanger 100 of the second embodiment is improved by 0.1% in year-round energy consumption efficiency as compared with the aspect of the first embodiment. In this way, by forming the cut and raised pieces 11B in the fins 30, the heat transfer performance of the flat tube heat exchanger 100 can be further improved.
  • FIG. 10 is a cross-sectional view of the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to the third embodiment.
  • FIG. 10 is a cross-sectional view in a cross section parallel to the extending direction of the fin 30.
  • the same components as those in the first embodiment will be described with the same reference numerals, and the description will focus on the parts different from the first and second embodiments.
  • the cut and raised pieces 11C and the heat exchange cut and raised pieces 12C have the same shapes as the cut and raised pieces 11 and the heat exchange cut and raised pieces 12 described in the first embodiment. The position is different.
  • the distance between the second virtual surface PL2 and the cut and raised piece 11C is larger than the distance between the second virtual surface PL2 and the cut and raised piece 12C for heat exchange. That is, when the distance between the second virtual plane PL2 and the center line of the cut and raised piece 11C is b1, and b2 is the distance between the second virtual plane PL2 and the center line of the heat exchange cut and raised piece 12, b1 > B2.
  • the cut and raised pieces 11C are described as having the same shape as the cut and raised pieces 11 described in the first embodiment, but the present invention is not limited thereto.
  • the cut and raised piece 11C may have the same shape as the cut and raised piece 11B described in the second embodiment.
  • FIG. 11 is a diagram showing the relationship between the amount of water remaining on the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to Embodiment 3 of the present invention and time.
  • the center line of the cut and raised piece 11C coincides with the center line of the cut and raised piece 12C for heat exchange
  • the condensed water drawn into the cut and raised piece 11C from the lower surface SF2 of the first flat tube 10A1 is heated.
  • the cut and raised piece 12C for replacement may be pulled into the replacement. That is, there is a case where the condensed water remaining on the cut and raised pieces 11C may be drawn into the heat exchange cut and raised pieces 12C due to the action of the capillaries resulting from the heat exchange cut and raised pieces 12C.
  • the center line of the cut and raised piece 11C is shifted from the center line of the heat exchange cut and raised piece 12C.
  • the distance between the second virtual surface PL2 and the cut and raised piece 11C is larger than the distance between the second virtual surface PL2 and the cut and raised piece 12C for heat exchange.
  • the condensed water drained from the cut and raised piece 11C is suppressed from being drawn into the heat exchange cut and raised piece 12, and the condensed water drained from the cut and raised piece 11C is more reliably guided to the drainage channel 13. be able to.
  • the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100 ⁇ / b> A according to the third embodiment has a water amount M that is faster than the aspect of the second embodiment (see the broken line in FIG. 11). It turns out that it decreases.
  • FIG. 12 shows the improvement rate of the heat transfer performance ⁇ o by forming the cut and raised pieces 11C and the heat raised and raised pieces 12C in the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to Embodiment 3 of the present invention.
  • FIG. 12 By making the distance between the second virtual surface PL2 and the cut-and-raised piece 11C larger than the distance between the second virtual surface PL2 and the cut-and-raised piece 12C for heat exchange, the flow on the surface of the fin 30 is further localized. Therefore, the amount of heat exchange between the air and the flat tube heat exchanger 100 is improved.
  • the flat tube heat exchanger 100 of the third embodiment has a heat transfer performance ⁇ o improved by about 5.0% as compared with the aspect of the second embodiment.
  • FIG. 13 shows the improvement rate of year-round energy consumption efficiency by forming the cut and raised pieces 11C and the heat raised and raised pieces 12C in the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to Embodiment 3 of the present invention.
  • FIG. 13 By forming the cut and raised pieces 11C and the heat exchange cut and raised pieces 12C, ventilation resistance generated when air passes through the flat tube heat exchanger 100 is also increased.
  • the energy consumption efficiency is improved because the contribution of the effect of improving the heat transfer performance is significant.
  • the flat tube heat exchanger 100 of the third embodiment is improved in energy consumption efficiency by about 0.2% throughout the year as compared with the aspect of the second embodiment.
  • the heat transfer performance of the flat tube heat exchanger 100 can be further improved by forming the cut and raised pieces 11C and the heat exchange cut and raised pieces 12C on the fins 30.
  • FIG. 14 is a cross-sectional view of flat tube heat exchanger 100 of refrigeration cycle apparatus 100A according to the fourth embodiment.
  • FIG. 14 is a cross-sectional view in a cross section parallel to the extending direction of the fin 30.
  • the same components as those in the first embodiment will be described with the same reference numerals, and the description will focus on parts different from the first to third embodiments.
  • the long axis AX1 of the first flat tube 10A1 and the long axis AX2 of the second flat tube 10A2 are parallel to the horizontal direction.
  • the long axis AX1 of the first flat tube 10A1 and the long axis AX2 of the second flat tube 10A2 intersect with the horizontal direction.
  • the long axis AX1 is a long axis in a cross section of the first flat tube 10A1 parallel to the extending direction of the fins 30.
  • the long axis AX1 corresponds to the first long axis.
  • the long axis AX2 is a long axis in a cross section of the second flat tube 10A2 parallel to the extending direction of the fins 30.
  • the long axis AX2 corresponds to the second long axis.
  • the flat tube heat exchanger includes plate-like fins 30 and heat transfer tubes 10.
  • the heat transfer tube 10 is disposed at a distance below the first flat tube 10A1 provided to intersect the fins 30 and below the first flat tube 10A1 and is provided to intersect the fins 30.
  • the first flat tube 10A1 is connected to the fins 30 and the second flat tube 10A2 is also connected to the fins 30.
  • the first end E1 located on the air inflow side is disposed below the second end E2 located on the air outflow side. That is, the long axis AX1 of the first flat tube 10A1 is not parallel to the horizontal direction but intersects the horizontal direction.
  • the major axis AX1 and the horizontal direction form an angle ⁇ .
  • the third end E3 located on the air inflow side is disposed below the fourth end E4 located on the air outflow side.
  • the first flat tube 10A1 and the second flat tube 10A2 are parallel to each other. That is, the long axis AX1 of the first flat tube 10A1 and the long axis AX2 of the second flat tube 10A2 are arranged in parallel to each other.
  • the long axis AX2 of the second flat tube 10A2 and the horizontal direction form an angle ⁇ .
  • the fin 30 is cut and raised at a position between the first flat tube 10A1 and the second flat tube 10A2 to form a piece 11D.
  • the formation position of the cut and raised piece 11D is the first region RE1 as described in the first to third embodiments.
  • the definition of the fourth virtual plane PL4 is different from those in the first to third embodiments.
  • the fourth virtual surface PL4 is a surface that is parallel to the gravity direction g and passes through the first end E1 of the first flat tube 10A1.
  • the first region RE1 is formed within a range defined by the first virtual surface PL1, the second virtual surface PL2, the third virtual surface PL3, and the fourth virtual surface PL4.
  • the cut and raised piece 11D is formed at a position near the drainage channel 13 in the first region RE1.
  • the cut-and-raised piece 12D for heat exchange is formed in the position between 1st flat tube 10 A1 and 2nd flat tube 10 A2.
  • the formation position of the heat exchange cut-and-raised piece 12D is the second region RE2.
  • the definition of the sixth virtual plane PL6 is different from those in the first to third embodiments.
  • the sixth virtual plane PL6 is a plane that is parallel to the gravity direction g and passes through the third end E3 of the second flat tube 10A2.
  • the second region RE2 is formed within a range defined by the first virtual surface PL1, the second virtual surface PL2, the fifth virtual surface PL5, and the sixth virtual surface PL6.
  • the heat exchange cut-and-raised piece 12D is formed at a position near the drainage channel 13 in the second region RE2.
  • the reason why the definitions of the fourth virtual surface PL4 and the sixth virtual surface PL6 are different from those in the first embodiment is that, in the fourth embodiment, the long axis AX1 and the first axis AX1 of the first flat tube 10A1. This is because the long axis AX2 of the two flat tubes 10A2 is in the form of intersecting in the horizontal direction.
  • the definitions of the fourth virtual surface PL4 and the sixth virtual surface PL6 change, and the shapes of the first region RE1 and the second region RE2 are also different from those of the first embodiment. That is, the first region RE1 and the second region RE2 in the first embodiment are rectangular, but the first region RE1 and the second region RE2 in the fourth embodiment are trapezoidal.
  • the seventh virtual surface PL7 and the eighth virtual surface PL8 are also different from the first to third embodiments.
  • the seventh virtual plane PL7 is a plane that is parallel to the gravity direction g and passes through the second end E2 of the first flat tube 10A1.
  • the eighth virtual plane PL8 is a plane that is parallel to the gravity direction g and passes through the fourth end E4 of the second flat tube 10A2.
  • the third region RE3 is a portion defined by the first virtual surface PL1, the second virtual surface PL2, the third virtual surface PL3, and the seventh virtual surface PL7.
  • the fourth region RE4 is a portion partitioned by the first virtual surface PL1, the second virtual surface PL2, the fifth virtual surface PL5, and the eighth virtual surface PL8.
  • the third region RE3 and the fourth region RE4 are both flat, and no cut and raised pieces are formed. By forming the cut and raised pieces, the pressure loss of the air passing through the fins 30 is prevented from increasing.
  • FIG. 15 is a diagram showing the relationship between the amount of water remaining on the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to Embodiment 4 and time.
  • the long axis AX1 of the first flat tube 10A1 and the long axis AX2 of the second flat tube 10A2 intersect with the horizontal direction. Therefore, the dew condensation water on the upper surface SF1 of the first flat tube 10A1 and the upper surface SF3 of the second flat tube 10A2 flows into the drainage channel 13 together with the dew condensation water flowing from the fins 30 and the like.
  • Condensed water on the lower surface SF2 of the first flat tube 10A1 moves closer to the first end E1 by the action of gravity, and then cuts and raises to the cut piece 11 by the action of the capillary tube by the cut and raised piece 11D. Be drawn. Then, the condensed water drawn into the cut and raised piece 11 ⁇ / b> D flows into the drainage channel 13. In this way, the condensed water on the lower surface SF2 of the first flat tube 10A1 is also quickly guided to the drainage channel 13.
  • the cut and raised pieces 12D for heat exchange are formed separately from the cut and raised pieces 11D. That is, the cut and raised piece 11D and the heat exchange cut and raised piece 12D are not integrally but a divided cut and raised piece. For this reason, it is possible to prevent the surface tension acting on the dew condensation water drawn into the cut and raised pieces 11D from becoming too large, and the dew condensation water of the cut and raised pieces 11D can be quickly flowed to the drainage channel 13.
  • the heat exchange cut and raised piece 12 may be formed larger than the cut and raised piece 11. Thereby, it is possible to prevent the cut and raised piece 11 from becoming too large and the surface tension of the condensed water adhering to the cut and raised piece 11 from being excessively increased, and the heat exchange performance of the heat exchange cut and raised piece 12. Can be improved. That is, the heat exchange performance of the fins 30 can be improved while avoiding the deterioration of the drainage performance of the cut and raised pieces 11D.
  • the amount of water M decreases immediately.
  • the flat tube heat exchanger is in a mode in which the long axis AX1 of the first flat tube 10A1 and the long axis AX2 of the second flat tube 10A2 are parallel to the horizontal direction, as shown by the broken line in FIG. It can be seen that the decrease in the amount of water M is slow.
  • FIG. 20 is a cross-sectional view in a cross section parallel to the extending direction of the fin 30. As shown in FIG. 20, the air toward the first end E1 is less likely to flow along the lower surface SF2 of the first flat tube 10A1 when reaching the first end E1.
  • the air that has collided with the first end E1 and the air that has reached the periphery of the first end E1 is peeled off from the lower surface SF2 and flows downstream.
  • the air separated from the lower surface SF2 flows near the second flat tube 10A2. That is, the amount of air flowing in the second region RE2 is greater than that in the first region RE1. Therefore, the heat exchange efficiency of the flat tube heat exchanger 100 can be efficiently improved by disposing the heat exchange cut and raised pieces 12 in the second region RE2.
  • FIG. 16 is a diagram showing the improvement rate of the heat transfer performance ⁇ o by forming the cut and raised pieces 11D and the heat exchange cut and raised pieces 12D in the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to the fourth embodiment. It is. In the flat tube heat exchanger 100, the heat exchange capability is reduced due to the separation of air around the first flat tube 10A1. However, the heat transfer promoting effect by the heat exchanging and raising pieces 12 is also produced. Since the heat transfer acceleration effect is greater than the heat exchange capacity decrease, the heat transfer performance ⁇ o is improved. As shown in FIG.
  • the flat tube heat exchanger has a longer axis AX1 of the first flat tube 10A1 and a longer axis AX2 of the second flat tube 10A2 than the aspect in which it is parallel to the horizontal direction. It can be seen that the heat transfer performance ⁇ o is improved by about 2.0%.
  • FIG. 17 is a diagram showing a year-round energy consumption efficiency improvement rate by forming the cut and raised pieces 11D and the heat exchange cut and raised pieces 12D in the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to the fourth embodiment. It is. By forming the cut and raised pieces 11D and the heat exchange cut and raised pieces 12D, ventilation resistance generated when air passes through the fins 30 of the flat tube heat exchanger 100 is also increased. However, considering the year-round energy consumption efficiency, the contribution of the effect of improving the heat transfer performance is large, so the year-round energy consumption efficiency is improved. As shown in FIG.
  • the flat tube heat exchanger is compared with a mode in which the long axis AX1 of the first flat tube 10A1 and the long axis AX2 of the second flat tube 10A2 are parallel to the horizontal direction.
  • energy consumption efficiency is equivalent. This is equivalent to the deterioration of the ventilation resistance due to the formation of the cut and raised pieces 11D and the heat raised cut and raised pieces 12D, and the heat transfer promotion effect due to the formation of the cut and raised pieces 11D and the heat exchange cut and raised pieces 12D. It is that.
  • FIG. 18 is a cross-sectional view of the cut and raised pieces 11D and the heat raised and raised pieces 12D formed in the flat tube heat exchanger 100 of the refrigeration cycle apparatus 100A according to the fourth embodiment.
  • the height h of the heat exchange cut and raised pieces 12D and the pitch FP of the fins 30 may be set as follows. That is, the height h of the cut and raised pieces of the heat exchange cut and raised pieces 12 ⁇ / b> D may be less than or equal to half the pitch FP of the fins 30.
  • the height h corresponds to the Y direction in FIG. 1B.
  • FIG. 19 is a diagram showing the relationship between the height h formed in the flat tube heat exchanger of the refrigeration cycle apparatus 100A according to Embodiment 4 and the heat transfer performance ⁇ o.
  • the slit height should be 1 ⁇ 2FP or less. Therefore, in the modification of the fourth embodiment, the height h is set to be equal to or less than half the pitch FP of the fins 30.
  • the configuration described in the second and third embodiments may be applied to the fourth embodiment. That is, the cut-and-raised piece 11D described in the fourth embodiment is drained from the portion near the first flat tube 10A1 toward the portion near the second flat tube 10A2 as in the second embodiment. 13 may be formed so as to approach 13. Further, as in the third embodiment, the distance between the second virtual surface PL2 and the cut-and-raised piece 11D is larger than the distance between the second virtual surface PL2 and the cut-and-raised piece 12D for heat exchange. May be.
  • the refrigeration cycle apparatus described in each embodiment is applied to an apparatus equipped with a refrigeration cycle, such as an air conditioner (for example, a refrigeration apparatus, a room air conditioner, a packaged air conditioner, a multi air conditioner for buildings), a heat pump water heater, and the like. Can be used.
  • a refrigeration cycle such as an air conditioner (for example, a refrigeration apparatus, a room air conditioner, a packaged air conditioner, a multi air conditioner for buildings), a heat pump water heater, and the like. Can be used.

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

Abstract

Selon l'invention, une pièce découpée et surélevée est disposée dans une première région divisée au moyen d'un premier plan virtuel, un deuxième plan virtuel, un troisième plan virtuel et un quatrième plan virtuel. Le premier plan virtuel est un plan passant à travers le centre entre un premier tube plat et un second tube plat et parallèle au premier axe longitudinal. Le deuxième plan virtuel est un plan passant à travers le centre de la largeur du premier axe longitudinal et le centre de la largeur d'un second axe longitudinal. Le troisième plan virtuel est un plan parallèle au premier axe longitudinal et passant à travers la face inférieure du premier tube plat. Le quatrième plan virtuel est un plan parallèle à la direction de la gravité et passant à travers une première extrémité du premier tube plat.
PCT/JP2016/052764 2016-01-29 2016-01-29 Dispositif à cycle frigorifique et échangeur de chaleur à tubes plats WO2017130399A1 (fr)

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JP2017563643A JP6548749B2 (ja) 2016-01-29 2016-01-29 冷凍サイクル装置及び扁平管熱交換器

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US10619930B2 (en) * 2016-09-23 2020-04-14 Daikin Industries, Ltd. Heat exchanger
WO2020250953A1 (fr) * 2019-06-12 2020-12-17 ダイキン工業株式会社 Conditionneur d'air
JP7468721B2 (ja) 2019-03-26 2024-04-16 株式会社富士通ゼネラル 熱交換器、及び熱交換器を備える空気調和機

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JPH0791873A (ja) * 1993-09-20 1995-04-07 Hitachi Ltd フィンアンドチューブ形熱交換器
JP2008002746A (ja) * 2006-06-22 2008-01-10 Kenji Umetsu 高性能空気熱交換器
EP2725311A2 (fr) * 2012-10-29 2014-04-30 Samsung Electronics Co., Ltd Échangeur de chaleur
JP2015132468A (ja) * 2015-04-22 2015-07-23 三菱電機株式会社 空気調和機の熱交換器

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GB2095813A (en) * 1981-02-05 1982-10-06 Hutogepgyar Engine cooler
JPH0791873A (ja) * 1993-09-20 1995-04-07 Hitachi Ltd フィンアンドチューブ形熱交換器
JP2008002746A (ja) * 2006-06-22 2008-01-10 Kenji Umetsu 高性能空気熱交換器
EP2725311A2 (fr) * 2012-10-29 2014-04-30 Samsung Electronics Co., Ltd Échangeur de chaleur
JP2015132468A (ja) * 2015-04-22 2015-07-23 三菱電機株式会社 空気調和機の熱交換器

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Publication number Priority date Publication date Assignee Title
US10619930B2 (en) * 2016-09-23 2020-04-14 Daikin Industries, Ltd. Heat exchanger
JP7468721B2 (ja) 2019-03-26 2024-04-16 株式会社富士通ゼネラル 熱交換器、及び熱交換器を備える空気調和機
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WO2020250953A1 (fr) * 2019-06-12 2020-12-17 ダイキン工業株式会社 Conditionneur d'air
JP2020201013A (ja) * 2019-06-12 2020-12-17 ダイキン工業株式会社 空調機
EP3961124A4 (fr) * 2019-06-12 2022-06-22 Daikin Industries, Ltd. Conditionneur d'air

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