WO2014115240A1 - 冷媒分配器及びこの冷媒分配器を用いたヒートポンプ装置 - Google Patents
冷媒分配器及びこの冷媒分配器を用いたヒートポンプ装置 Download PDFInfo
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- WO2014115240A1 WO2014115240A1 PCT/JP2013/051146 JP2013051146W WO2014115240A1 WO 2014115240 A1 WO2014115240 A1 WO 2014115240A1 JP 2013051146 W JP2013051146 W JP 2013051146W WO 2014115240 A1 WO2014115240 A1 WO 2014115240A1
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- refrigerant
- distributor
- branch pipe
- way branch
- tube
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Classifications
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/028—Evaporators having distributing means
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
- F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
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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
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
- F28D1/0476—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2275/00—Fastening; Joining
- F28F2275/04—Fastening; Joining by brazing
Definitions
- the present invention relates to a refrigerant distributor.
- a refrigerant distributor that distributes the refrigerant to each path is provided on the refrigerant inlet side. is necessary.
- a distributor has been used as a refrigerant distributor, and each refrigerant distributed by the distributor is caused to flow into each heat transfer tube of the heat exchanger through a capillary tube (for example, see Patent Document 1).
- Patent Document 1 a plurality of heat transfer tubes are connected to distributors through the capillary tubes, and the end portions serving as refrigerant inlets from the outside are individually connected, and the number of heat exchanger passes and the number of capillary tubes are the same. It is. For this reason, when the number of heat transfer tubes increases and the number of passes increases, the number of capillary tubes also increases accordingly.
- the present invention has been made in view of the above points, a refrigerant distributor capable of reducing the number of connections of capillary tubes, reducing the installation space when mounting the capillary tubes on an actual machine, and reducing the cost, and the refrigerant.
- a heat pump device using a distributor is provided.
- a refrigerant distributor is a refrigerant distributor for distributing refrigerant to a plurality of heat transfer tubes constituting a heat exchanger, the first distributor for distributing the refrigerant into a plurality of parts, and the first distributor And a plurality of second distributors for branching the refrigerant distributed by the distributor into two and allowing the refrigerant to flow into the two heat transfer tubes.
- the number of capillary tubes connected can be reduced, and the installation space for mounting the capillary tubes on an actual machine can be made compact and the cost can be reduced.
- FIG. 1 It is the schematic block diagram which showed the state which connected the refrigerant distributor which concerns on Embodiment 1 of this invention to the heat exchanger. It is a perspective view of the two-way branch pipe of FIG. It is a perspective view of a circular tube-flat tube joint. It is structure explanatory drawing of the two-way branch pipe of the refrigerant distributor which concerns on Embodiment 1 of this invention. It is a figure which shows the refrigerant circuit of the heat pump apparatus with which the refrigerant distributor which concerns on Embodiment 1 of this invention is used.
- FIG. 13 (A) It is a figure which shows the structural example which used the header for the 1st divider
- FIG. 1 is a schematic configuration diagram illustrating a state in which the refrigerant distributor according to Embodiment 1 of the present invention is connected to a heat exchanger.
- the same reference numerals denote the same or corresponding parts, which are common throughout the entire specification.
- the forms of the constituent elements appearing in the entire specification are merely examples and are not limited to these descriptions.
- the heat exchanger 1 includes a plurality of plate-like fins 2 stacked at intervals, and a fin-and-tube provided with a plurality of heat transfer tubes 3 that penetrate the plate-like fins 2 in the stacking direction and in which refrigerant flows. It is a heat exchanger.
- the heat transfer tube 3 is a copper or aluminum circular tube, a flat tube, or the like.
- a refrigerant distributor 10 is connected to one end side of the plurality of heat transfer tubes 3, and a gas header 6 is connected to the other end side.
- the refrigerant distributor 10 includes a first distributor 20 and a plurality of two-way branch pipes 30 as second distributors.
- the first distributor 20 is required to evenly branch the refrigerant that has flowed into the first distributor 20 in the gas-liquid two-phase state to the heat transfer tubes 3 of the heat exchanger 1. For this reason, a distributor is used as the first distributor 20 in FIG.
- ⁇ A throttling mechanism such as an orifice is inserted inside the distributor, and the two-phase flow that has flowed in is passed through the orifice to create a spray flow state that facilitates even distribution.
- the sprayed refrigerant is evenly distributed to each capillary tube 40.
- the distributor may have a specification that does not have a restriction mechanism such as an orifice inserted therein.
- the first distributor 20 may be a distributor capable of even distribution.
- the material of the distributor is made of copper, aluminum, brass or the like.
- a capillary tube 40 having an inner diameter of about 3.5 mm and a length of about 1000 mm is used.
- the above dimensions of the capillary tube 40 are just an example.
- the capillary tube 40 may be bent in a circular shape due to the relationship between the length and the installation space.
- the capillary tube 40 can adjust the pressure loss in the pipe according to its specifications (inner diameter, length), and can adjust the diversion ratio from the first distributor 20 to each of the two-way branch pipes 30.
- the wind speed from a blower fan (not shown) that blows air to the heat exchanger 1 is not necessarily uniform over the entire surface of the heat exchanger 1, and a wind speed distribution may exist. For example, when a blower fan is installed in the upper part of the heat exchanger 1, the wind speed is faster in the upper part of the heat exchanger 1 than in the lower part.
- the refrigerant passing through the portion where the wind speed is fast is more easily gasified and easily dried than the refrigerant passing through the portion where the wind speed is slow. Therefore, when the amount of refrigerant flowing into each heat transfer tube 3 is the same, the refrigerant that has passed through the portion with the high wind speed has a higher dryness than the refrigerant that has passed through the portion with the low wind speed, and the refrigerant state varies at the outlet of the heat exchanger. Occurs, and the refrigerant state becomes unstable. Therefore, it is required to divert so that a large amount of refrigerant flows into the heat transfer tube located in the portion where the wind speed is high. Thus, when it is required to adjust the flow dividing ratio, the flow dividing ratio can be adjusted by adjusting the specifications of the capillary tube 40.
- a two-way branch pipe 30 is connected to the end of the capillary tube 40 opposite to the first distributor 20.
- the two-way branch pipe 30 it is possible to distribute the refrigerant to a 2 ⁇ A branch number (pass number), where A is the number of branches of the first distributor 20 and the number of capillary tubes 40.
- a branch number bypass number
- FIG. 2 is a perspective view of the two-way branch pipe of FIG.
- the two-way branch pipe 30 has a U-bend part 31 formed by bending a circular pipe into a U shape, and a straight inflow part 35.
- the U-bend portion 31 includes a connecting portion 32 and two arm portions 33 and 34 that extend in parallel from both ends of the connecting portion 32.
- the straight inflow portion 35 is formed by bulging one of the two arm portions 33, 34 of the U bend portion 31 (here, the arm portion 34).
- the example which provided the linear inflow part 35 in the arm part 34 side is shown.
- a pipe-shaped material is first set in a mold in a press and then clamped. And it is a processing method that stretches the material to the shape carved in the mold and compresses it by compressing in the axial direction so that both ends of the material approach each other while filling the material with high pressure liquid .
- One end of an L-shaped tube 36 bent in an L-shape is attached to the linear inflow portion 35 of the two-way branch tube 30 thus configured, and the other end of the L-shaped tube 36 is connected to the capillary tube 40. Is done.
- the openings A and B of the two arm portions 33 and 34 of the two-way branch tube 30 are connected to the heat transfer tube 3 of the heat exchanger 1.
- the connection between the two arm portions 33 and 34 and the heat transfer tube 3 is directly connected if the heat transfer tube 3 is a circular tube, and the circular tube-flat tube joint shown in FIG. 3 if the heat transfer tube 3 is a flat tube. 4 is connected.
- the two-way branch pipe 30 is connected to the heat exchanger 1 so that the two arm portions 33 and 34 are along the horizontal direction, and the refrigerant flowing into the arm portion 34 from the linear inflow portion 35 branches in the horizontal direction. And make it flow. The reason will be described later.
- the dotted arrows indicate the flow of refrigerant when the heat exchanger 1 is used as an evaporator, and the refrigerant flowing from the capillary tube 40 passes through the L-shaped pipe 36 in the two-way branch pipe 30. It flows into the linear inflow part 35 via.
- the refrigerant that has flowed into the straight inflow portion 35 is branched into two, that is, the arm portion 33 side and the arm portion 34 side, and each flows into each heat transfer tube 3.
- the two-way branch pipe 30 branches the refrigerant that has flowed into two and flows into each heat transfer pipe 3, compared to the configuration in which the capillary tube 40 is directly connected to each heat transfer pipe 3, The number of capillary tubes 40 can be reduced to half. Therefore, the installation property of the capillary tube 40 can be improved by using the refrigerant distributor 10 of the first embodiment.
- the two-way branch pipe 30 is required to have a function of distributing the refrigerant flowing in from the capillary tube 40 and flowing it into each heat transfer pipe 3 in addition to improving the installation property of the capillary tube 40.
- the refrigerant can be evenly distributed to the capillary tubes 40 in the first distributor 20, but finally flows into the heat transfer tubes of the heat exchanger 1 while maintaining the equal distribution state. It is necessary to distribute evenly even in the two-way branch pipe 30 portion.
- the refrigerant that has passed through the expansion valve of the heat pump device and the refrigerant at the inlet of the evaporator are in a gas-liquid two-phase state of a gas refrigerant and a liquid refrigerant, and a density distribution occurs in the cross section of the refrigerant flowing in the pipe.
- a drift phenomenon occurs in which the liquid refrigerant is biased toward the inner surface of one of the pipes due to the centrifugal force. That is, the two-phase refrigerant is gas-liquid separated.
- the refrigerant distributor located on the inflow side is required to have a function that prevents the above-described drift phenomenon and prevents the gas and liquid from separating. .
- the refrigerant distributor has a function of distributing the refrigerant in a state where the refrigerant is homogeneously mixed and the gas-liquid mass flow ratio at the refrigerant distributor inlet and the gas-liquid mass flow ratio at the refrigerant distributor outlet are equal. Required. Further, as described above, when the number of passes increases due to the diameter reduction and flattening of the circular tube, it becomes an even more important issue to branch a uniform refrigerant flow rate into each pass.
- FIG. 4 is an explanatory diagram of the structure of the two-way branch pipe of the refrigerant distributor according to Embodiment 1 of the present invention.
- (a) is a front view of the two-way branch pipe 30, and
- (b) is a side view of (a).
- the straight inflow portion 35 bulged in the two-way branch pipe 30 is shaped such that the angle ⁇ 1 between the pipe axis X1 and the pipe axis X2 of the arm portion 34 is 90 degrees.
- the angle ⁇ 1 deviates from 90 degrees by 10 degrees or more, the refrigerant flowing from the linear inflow portion 35 obliquely collides with the portion of the arm portion 34 facing the linear inflow portion 35 and drifts, and heat exchange occurs. Efficiency will deteriorate. Therefore, the angle theta 1 is 90 degrees. In addition, it is not limited to perfect 90 degree
- the length of the linear inflow portion 35 is 5 mm or more, it is more effective for uniform distribution. This point will be described.
- the refrigerant two-phase flow is in a state where the liquid portion of the refrigerant is biased to one end by the capillary tube 40. Therefore, a sufficiently stable flow can be obtained by setting the running section until the collision that branches into two branches to 20 times or more of the inner diameter.
- the length of the linear inflow portion 35 is ensured to be 5 mm or more, and the distance between the capillary tube 40 or the horizontal portion of the L-shaped tube 36 is 15 mm or more (more than twice the inner diameter). ) Secure.
- the gas-liquid two-phase flow is affected by the bending of the capillary tube 40, and the liquid level in the tube of the linear inflow portion 35 is biased.
- the gas-liquid two-phase flow that has flowed into the straight inflow portion 35 drifts due to the influence of the unevenness of the liquid level, cannot be evenly distributed by the two-way branch pipe 30, and the heat exchange efficiency deteriorates. .
- the angle theta 1 of the arm portion 34 of the straight inlet section 35 with a 90 ° it is preferably not less than 5mm in length of the linear inlet portion 35.
- a straight inlet section 35 of the 2-way branch pipe 30 have been described above points to bulge forming, by using the bulge forming process, the angle theta 1 is able to stably processing a 90 degree geometry, and, The straight inflow portion 35 can be secured longer than 5 mm.
- the bulge forming process can be applied to a bent pipe instead of a straight line, and the linear inflow portion 35 can be formed long while suppressing the thinning.
- an L-shaped pipe 36 or a capillary tube 40 having an outer diameter smaller than the inner diameter of the inlet is formed at the inlet of the bulge-formed straight inlet 35. Insert and braze. By manufacturing in this way, it is possible to manufacture stably without defects.
- the linear inflow portion 35 is formed without using bulge forming, the length of the linear inflow portion 35 is shortened and the thickness of the linear inflow portion 35 is reduced. Then, when joining the L-shaped tube 36 or the capillary tube 40 in a straight line inlet portion 35, the angle theta 1 is shifted more than 90 degrees.
- the straight inflow portion 35 becomes a brazing region during brazing joining, stable brazing cannot be performed due to thinning and the short joint length.
- the angle ⁇ 2 of the linear inflow portion 35 around the tube axis X2 of the arm portion 34 may be any number, but here, ⁇ 2 is set to 90 degrees as shown in FIG. .
- ⁇ 2 is set to 90 degrees as shown in FIG. .
- the installation property of the capillary tube 40 can be improved as described above, but the angle ⁇ 2 (described in FIG. 4) of the linear inflow portion 35 of the two-way branch pipe 30 is 90 degrees. By doing so, the connectivity of the capillary tube 40 can be further improved.
- the L-shaped pipe 36 and the straight inflow part 35 of the two-way branch pipe 30 are brazed in advance, and then the openings A and B are brazed to the circular pipe-flat pipe joint 4 respectively.
- the brazing here is based on the premise of the burner brazing, and finally the L-shaped tube 36 and the capillary tube are brazed and joined, so that the fire of the burner hardly hits other piping.
- the capillary tube 40 is directly connected to the linear inflow portion 35 of the two-way branch tube 30, so that the capillary tube 40 is long, has poor stability, and is difficult to handle.
- the variation in the angle ⁇ 1 flowing into the lens 30 tends to increase.
- the straight inflow portion 35 of the two-way branch pipe 30 is set to 5 mm or more.
- the L-shaped pipe 36 and the straight inflow portion are only required to have a straight flow path of 10 mm or more. It is good also as 10 mm or more in total with 35.
- FIG. 5 is a diagram showing a refrigerant circuit of the heat pump device in which the refrigerant distributor according to Embodiment 1 of the present invention is used.
- the heat pump device 60 includes a compressor 61, a condenser 62 (heat exchanger 1), an expansion valve 63 as a decompression device, and an evaporator 64 (heat exchanger 1).
- the gas refrigerant discharged from the compressor 61 flows into the condenser 62, exchanges heat with the air passing through the condenser 62, and flows out as high-pressure liquid refrigerant.
- the high-pressure liquid refrigerant that has flowed out of the condenser 62 is decompressed by the expansion valve 63 to become a low-pressure gas-liquid two-phase refrigerant and flows into the evaporator 64.
- the low-pressure gas-liquid two-phase refrigerant flowing into the evaporator 64 exchanges heat with the air passing through the evaporator 64 to become a low-pressure gas refrigerant, and is sucked into the compressor 61 again.
- FIG. 1 the solid line arrows indicate the flow of the refrigerant when the heat exchanger 1 is used as an evaporator.
- the gas-liquid two-phase refrigerant flow flowing out from the expansion valve 63 first flows into the first distributor 20 and is sprayed.
- the sprayed refrigerant flows evenly into each capillary tube 40 and flows.
- Each refrigerant that has passed through each capillary tube 40 flows into the two-way branch tube 30, is equally branched into two as described above, flows out, and flows into the heat transfer tube 3.
- the refrigerant that has flowed into each heat transfer tube 3 exchanges heat with air to become a gas state, and merges at the gas header 6.
- the refrigerant merged in the gas header 6 is sucked into the compressor 61.
- FIG. 1 dotted arrows indicate the flow of refrigerant when the heat exchanger 1 is used as a condenser.
- the refrigerant flow direction is opposite to that in the case of the evaporator, and the gas refrigerant flow flowing out of the compressor 61 flows into the gas header 6.
- the refrigerant flowing into the gas header 6 is equally distributed by the gas header 6 and flows into each heat transfer tube 3.
- each heat transfer tube 3 exchanges heat with air, and then flows in the order of the two-way branch tube 30, the capillary tube 40, and the first distributor 20. Then, they merge at the first distributor 20 and flow into the expansion valve 63.
- FIG. 6 is a diagram showing a configuration example in which the refrigerant distributor according to Embodiment 1 of the present invention is connected to a heat exchanger for an outdoor unit of an air conditioner using a flat tube as a heat transfer tube.
- FIG. 7 is an enlarged perspective view of the connection portion of the heat exchanger of FIG. 5 with the refrigerant distributor as viewed from the back side. In FIG. 7, the solid-coated portion is the two-way branch pipe 30.
- FIG. 8 is a perspective view of the flat tube of FIG.
- the heat exchanger 100 includes a plurality of plate-like fins 2 stacked at intervals and a plurality of flat tubes 3 that penetrate the plate-like fins 2 in the stacking direction and through which refrigerant flows. In addition, it has a configuration in which three rows are provided in the row direction which is the air passage direction. In addition to the two-way branch pipe 30, the hairpin bent bend 5 and gas header 6 are connected to the ends of the plurality of flat tubes 3. Further, in this heat exchanger 100, the flat tube 3 is used as the heat transfer tube, so the flat tube 3 is connected to the two-way branch tube 30 and the bend 5 via the circular tube-flat tube joint 4.
- the heat exchanger 100 when used as an evaporator, the heat exchanger 100 is a so-called parallel flow in which the refrigerant flows so that the refrigerant flow is folded from the upstream side to the downstream side with respect to the air flow direction.
- the path is assembled.
- the heat exchanger 100 when used as a condenser, a path is assembled so as to form a so-called counter flow in which the refrigerant flows in a manner that turns back from the downstream side to the upstream side with respect to the air flow direction. Since the refrigerant is subcooled in the condenser, the refrigerant temperature is lowered. For this reason, the heat exchange efficiency at the time of using the heat exchanger 100 as a condenser can be improved by carrying out path
- the plate-like fins 2 are made of aluminum, and the flat tubes 3 and the plate-like fins 2 are joined by brazing in the furnace.
- the heat transfer tubes and plate fins are joined by a mechanical expansion method, and there is an air layer between the heat transfer tubes and plate fins, so heat exchange efficiency deteriorates.
- heat exchange efficiency deteriorates.
- the flat tube 3 and the plate-like fin 2 are joined by brazing in the furnace, the thermal resistance between the flat tube 3 and the plate-like fin 2 becomes zero, and the heat exchange efficiency can be improved.
- the flat tube 3 is made of aluminum, and as shown in FIG. 8, the interior is partitioned to form a plurality of passages 31a, and the refrigerant flows through the passages 31a.
- the flat tube 3 can increase the refrigerant and contact heat transfer area three times or more compared to the circular tube.
- FIG. 9 is a view showing a conventional example in which a two-way branch pipe is not used in a three-row heat exchanger.
- the use of the two-way branch pipe 30 can reduce the number of capillary tubes 40 to half that of the conventional one.
- the refrigerant distributor 10 in which the two-way branch pipe 30 is combined with the capillary tube 40 that is the outflow pipe of the first distributor 20 is used.
- the number can be reduced. Therefore, the installation space of the capillary tube 40 when mounting the capillary tube 40 on an actual machine becomes compact. Further, the cost can be reduced by reducing the number of capillary tubes 40, and the actual machine can be configured at low cost.
- the angle theta 1 of the arm portion 34 of the straight inlet section 35 is 90 degrees, two-phase flow refrigerant vertically collide with the collision wall 34a opposed to the inlet portion, and the branch direction after collision horizontal Thus, it is not affected by gravity and can be distributed evenly regardless of the amount of circulation.
- the linear inlet portion 35 to form with a bulge forming process the angle theta 1 can be stably processed 90 degrees shape.
- the refrigerant two-phase flow that has flowed into the linear inflow portion 35 can collide with the collision wall 34a vertically as a stable annular flow, and variations in refrigerant distribution can be achieved. It can be suppressed and even distribution is possible.
- the heat exchanger 1 can sufficiently exhibit a predetermined heat exchange performance.
- Embodiment 2 the number of capillary tubes 40 is further reduced.
- the second embodiment will be described focusing on the differences from the first embodiment. Note that the modification applied to the same components as those in the first embodiment is similarly applied to the second embodiment.
- FIG. 10 is a configuration diagram of a refrigerant distributor according to Embodiment 2 of the present invention.
- 10A is a front view
- FIG. 10B is a cross-sectional view taken along the line AA in FIG.
- FIG. 11 is a diagram showing a third distributor in the refrigerant distributor of FIG.
- (a) is a front view of the refrigerant distributor 10A
- (b) is a side view of (a)
- (c) is a bottom view of (a).
- the refrigerant distributor 10A includes a two-way branch as a third distributor in addition to the first distributor 20 and the two-way branch pipe 30 as the second distributor in the first embodiment.
- the configuration includes a plurality of tubes 50.
- the two-way branch pipe 50 has the same structural features as the two-way branch pipe 30 of the first embodiment, and a U-bend portion 51 formed by bending a circular pipe into a U-shape, and a linear inflow portion 55. And have.
- the U-bend portion 51 includes a connecting portion 52 and two arm portions 53 and 54 that extend in parallel from both ends of the connecting portion 52.
- the straight inflow portion 55 is formed by bulging one of the two arm portions 53 and 54 of the U bend portion 51 (here, the arm portion 54).
- the straight inflow portion 55 of the two-way branch pipe 50 is connected to the capillary tube 40, and the two arm portions 53 and 54 are connected to the straight inflow portion 35 of the two-way branch pipe 30 adjacent to each other.
- the two-way branch pipe 50 is also installed so that the two arm portions 53 and 54 are along the horizontal direction.
- the refrigerant distributor 10A of the second embodiment configured as described above can obtain the same effects as those of the first embodiment and the following effects. That is, since the two-way branch pipe 50 is provided as the third distributor, the number of capillary tubes 40 connected to the first distributor 20 can be reduced to half that of the first embodiment.
- the two-way branch pipe 50 is an inflow pipe for the refrigerant that has flowed out of the capillary tube 40, the same function as the two-way branch pipe 30 of the first embodiment is required. That is, the function of distributing the refrigerant flowing in from the capillary tubes 40 evenly and flowing into the heat transfer tubes 3 is required. Since the two-way branch pipe 50 has the same configuration as the two-way branch pipe 30, the refrigerant flowing from the straight inflow portion 35 of the two-way branch pipe 50 is on the wall surface facing the straight inflow portion 55 in the arm portion 54. Collides vertically with a collision wall. And since the branch direction after a collision is a horizontal direction, it is not influenced by gravity, and equal distribution is attained irrespective of the circulation amount.
- Embodiment 3 relates to a refrigerant distributor that can adjust the distribution ratio of the refrigerant.
- the third embodiment will be described focusing on the differences from the first embodiment. Note that the modification applied to the same components in the third embodiment as those in the first embodiment is similarly applied to the third embodiment.
- FIG. 12 is a configuration diagram of a second distributor in the refrigerant distributor according to Embodiment 3 of the present invention.
- (a) is a front view of the second distributor
- (b) is a side view of (a).
- the refrigerant distributor of the third embodiment has a configuration provided with a two-way branch pipe 30A instead of the two-way branch pipe 30 of the first embodiment, and the other configuration is the same as that of the first embodiment.
- the angle theta 1 of the arm portion 34 of the straight inlet section 35 was 90 degrees.
- the angle theta 1 which was adjusted configuration angle corresponding to a desired distribution ratio.
- the angle ⁇ 1 is set to an angle smaller than 90 degrees, the flow rate of the refrigerant flowing to the opening A side is larger than the opening B side, and when the angle ⁇ 1 is set to an angle larger than 90 degrees, the opening A The flow rate of the refrigerant flowing to the opening B side is larger than the side.
- the linear inflow part 35 which requires angle adjustment is formed by a bulge forming process like the first embodiment.
- the angle ⁇ 2 may be any number as in the first embodiment, but is preferably 90 degrees in consideration of the connectivity of the capillary tube 40.
- the two-way branch pipe 30A has one end connected to the first distributor 20 and the other end connected to the other end of the capillary tube 40.
- the wind speed from the blower fan that blows air to the heat exchanger 1 is not necessarily uniform over the entire surface of the heat exchanger 1 as described above, and there is a wind speed distribution. Due to the difference in the wind speed distribution or the length of the refrigerant flow path per one heat path, the heat load may be different in each path. For this reason, among the paths connected to each of the opening A and the opening B, for example, a path having a higher wind speed or a path having a larger number of heat transfer tubes and a longer flow path length has a larger amount of refrigerant. Need to flow. Therefore, to determine the distribution ratio of the refrigerant to the opening A side and the opening side B in accordance with the thermal load distribution of each path in the heat exchanger 1, for determining the angle theta 1.
- the refrigerant flowing from the linear inflow portion 35 collides with the opposing surface of the linear inflow portion 35 at the angle ⁇ 1 and then the arm portion 33 according to the inclination angle ⁇ .
- the flow rate is adjusted and distributed to the side and the arm 34 side.
- coolant of each distributed flow volume flows in into each heat exchanger tube 3 of each path
- the number of capillary tubes 40 can be reduced as in the first embodiment, and a refrigerant distributor capable of adjusting the refrigerant distribution ratio can be obtained.
- Embodiment 4 relates to a refrigerant distributor that can adjust the distribution ratio of the refrigerant, as in the third embodiment.
- the difference between the fourth embodiment and the first embodiment will be mainly described. Note that the modification applied to the same components in the third embodiment as those in the first embodiment is similarly applied to the fourth embodiment.
- FIG. 13 is a configuration diagram of a second distributor in the refrigerant distributor according to Embodiment 4 of the present invention.
- 13A shows a configuration example of the two-way branch pipe 30B when the distribution ratio on the opening B side is larger than that on the opening A side
- FIG. 13B shows a configuration of the two-way branch pipe 30B in the opposite case.
- An example is shown.
- 13A and 13B (a) is a front view of the two-way branch pipe 30B, and (b) is a side view of (a).
- FIG. 14 is an enlarged view of a main part of FIG.
- the refrigerant distributor of the fourth embodiment has a configuration provided with a two-way branch pipe 30B instead of the two-way branch pipe 30 of the first embodiment, and the other configuration is the same as that of the first embodiment.
- the two-way branch pipe 30B is provided with a recess 37 recessed inwardly adjacent to the collision wall 34a.
- molding, and the point which may have any angle (theta) 2 are the same as that of Embodiment 1.
- the depression 37 is formed as shown in FIG. 37 is provided closer to the opening A than the collision wall 34 a in the tube axis direction of the U-bend portion 31.
- the heat load on the opening A side is high, that is, when it is desired to increase the refrigerant flow rate on the opening A side than on the opening B side, as shown in FIG.
- a recess 37 is provided on the opening B side of the collision wall 34a in the direction.
- the cross-sectional area of the passage becomes small, and the refrigerant after the collision hardly flows to the collision wall 34a. Therefore, in the case of FIG. 13A, the distribution ratio of the opening B can be made larger than the opening A, and in the case of FIG. 13B, the distribution of the opening A than the opening B can be achieved. The ratio can be increased.
- the depression 37 is not provided in the collision wall 34a facing the linear inflow portion 35. This is because the depression 37 is formed by using a press or a punch, and if the depression 37 is provided in the collision wall 34a, the linear inflow portion 35 may be deformed during the formation. In this way, by adopting a structure in which the depression 37 is not provided in the collision wall 34a facing the linear inflow portion 35, the inconvenience of deformation can be avoided, and the two-way branch pipe 30B can be manufactured stably.
- the number of the capillary tubes 40 can be reduced as in the first embodiment, and a refrigerant distributor capable of adjusting the refrigerant distribution ratio can be obtained.
- the first distributor 20 has been described as a distributor.
- the present invention is not limited to this, and a header 70 may be used as shown in FIG. In this case, the same effect as described above can be obtained.
- the heat exchanger described in the above embodiment and the air conditioner using the heat exchanger are soluble in the refrigerant and oil such as mineral oil, alkylbenzene oil, ester oil, ether oil, and fluorine oil.
- oil such as mineral oil, alkylbenzene oil, ester oil, ether oil, and fluorine oil. The effect can be achieved with any refrigeration oil, whether or not.
- the embodiments 1 to 4 have been described as different embodiments, the embodiments that can be combined may be appropriately combined.
- the second embodiment and the third embodiment may be combined to replace the two-way branch pipe 30 of the second embodiment shown in FIG. 10 with the two-way branch pipe 30A of the third embodiment.
- the present invention can be used for a heat exchanger of a heat pump device that requires improved heat exchange performance and improved performance.
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Abstract
Description
図1は、本発明の実施の形態1に係る冷媒分配器を熱交換器に接続した状態を示した概略構成図である。図1及び後述の図において、同一の符号を付したものは、同一の又はこれに相当するものであり、これは明細書の全文において共通している。更に、明細書全文に表れている構成要素の形態は、あくまで例示であってこれらの記載に限定されるものではない。
冷媒分配器10は、第1の分配器20と第2の分配器としての複数の2方分岐管30とを備えている。第1の分配器20には、気液二相状態で第1の分配器20に流入した冷媒を均等に熱交換器1の各伝熱管3に分岐することが求められる。このため、第1の分配器20として、図1ではディストリビュータを用いている。
2方分岐管30は、円管をU字状に折り曲げて形成されたUベンド部31と、直線状流入部35とを有している。Uベンド部31は、連結部32と、連結部32の両端から互いに並行に延びる2つの腕部33、34とを有している。直線状流入部35は、Uベンド部31の2つの腕部33、34のうちの一方(ここでは腕部34)をバルジ成形加工して形成されている。ここでは、腕部34側に直線状流入部35を設けた例を示している。バルジ成形加工とは、まずプレス内の金型にパイプ形状の素材をセット後、型締めする。そして、素材内に高圧の液体を充填しながら素材の両端を互いに近づくように軸方向に圧縮する事で、金型に彫られた形状に素材を伸ばして中空成形を行う加工法のことである。
2方分岐管30においてバルジ成形された直線状流入部35は、その管軸X1と腕部34の管軸X2との角度θ1 が90度になるように成形される。
ヒートポンプ装置60は、圧縮機61と、凝縮器62(熱交換器1)と、減圧装置としての膨張弁63と、蒸発器64(熱交換器1)とを備えている。圧縮機61から吐出されたガス冷媒は凝縮器62に流入し、凝縮器62を通過する空気と熱交換して高圧液冷媒となって流出する。凝縮器62を流出した高圧液冷媒は膨張弁63で減圧されて低圧の気液二相冷媒となり、蒸発器64に流入する。蒸発器64に流入した低圧の気液二相冷媒は、蒸発器64を通過する空気と熱交換して低圧ガス冷媒となり、再び圧縮機61に吸入される。
膨張弁63から流出した気液二相冷媒流は、まず第1の分配器20に流入して噴霧流化される。噴霧流化された冷媒は、各キャピラリーチューブ40に均等に分配されて流入する。各キャピラリーチューブ40を通過した各冷媒は2方分岐管30に流入し、上述したように均等に2つに分岐されて流出し、伝熱管3に流入する。各伝熱管3内に流入した冷媒は空気と熱交換してガス状態となり、ガスヘッダ6で合流する。ガスヘッダ6で合流した冷媒は、圧縮機61に吸入される。
凝縮器の場合は、蒸発器の場合と逆の冷媒流れ方向となり、圧縮機61から流出したガス冷媒流はガスヘッダ6内に流入する。ガスヘッダ6に流入した冷媒は、ガスヘッダ6で均等分配されて各伝熱管3に流入する。冷媒がガス状態の場合は均等分配が容易であるため、ディストリビュータ等は不要であり、円筒状の中空管で構成されたガスヘッダ6を用いるようにしている。
図7と図9とを比較して明らかなように、2方分岐管30を用いることにより、キャピラリーチューブ40の本数を、従来に比べて半数に削減することができる。
実施の形態2は、キャピラリーチューブ40の本数の更なる低減を図ったものである。以下、実施の形態2が実施の形態1と異なる部分を中心に説明する。なお、実施の形態1と同様の構成部分について適用される変形例は、本実施の形態2についても同様に適用される。
実施の形態3は、冷媒の分配比を調整できる冷媒分配器に関する。以下、実施の形態3が実施の形態1と異なる部分を中心に説明する。なお、実施の形態3において実施の形態1と同様の構成部分について適用される変形例は、本実施の形態3についても同様に適用される。
実施の形態3の冷媒分配器は、実施の形態1の2方分岐管30に代えて2方分岐管30Aを備えた構成を有し、それ以外の構成は実施の形態1と同様である。
実施の形態4は、実施の形態3と同様、冷媒の分配比を調整できる冷媒分配器に関する。以下、実施の形態4が実施の形態1と異なる部分を中心に説明する。なお、実施の形態3において実施の形態1と同様の構成部分について適用される変形例は、本実施の形態4についても同様に適用される。
Claims (10)
- 熱交換器を構成する複数の伝熱管に冷媒を分配するための冷媒分配器であって、
冷媒を複数に分配する第1の分配器と、
前記第1の分配器で分配された冷媒を2つに分岐して2つの前記伝熱管に流入させる複数の第2の分配器と
を備えたことを特徴とする冷媒分配器。 - 前記第2の分配器は2方分岐管で構成され、
前記2方分岐管は、
連結部及び前記連結部の両端から互いに並行に延びる2つの腕部を有するU字状のUベンド部と、
前記Uベンド部の前記2つの腕部のうちの一方をバルジ成形加工して形成された直線状流入部とを有する
ことを特徴とする請求項1記載の冷媒分配器。 - 熱交換器を構成する複数の伝熱管に冷媒を分配するための冷媒分配器であって、
冷媒を複数に分配する第1の分配器と、
冷媒を2つに分岐して2つの前記伝熱管に流入させる複数の第2の分配器と、
前記第1の分配器と前記第2の分配器との間に設けられ、前記第1の分配器で分配された冷媒を2つに分岐して、互いに隣接する2つの前記第2の分配器に流入させる複数の第3の分配器と
を有することを特徴とする冷媒分配器。 - 前記第2の分配器及び第3の分配器のそれぞれは2方分岐管で構成され、
前記2方分岐管は、
連結部及び前記連結部の両端から互いに並行に延びる2つの腕部を有するU字状のUベンド部と、
前記Uベンド部の前記2つの腕部のうちの一方をバルジ成形加工して形成された直線状流入部とを有する
ことを特徴とする請求項3記載の冷媒分配器。 - 前記2方分岐管は、
前記直線状流入部と、前記直線状流入部が形成された一方の前記腕部との角度が90度に形成されている
ことを特徴とする請求項2又は請求項4記載の冷媒分配器。 - 前記第2の分配器は、
前記直線状流入部が前記一方の前記腕部に対して傾斜して形成されていることを特徴とする請求項2又は請求項4記載の冷媒分配器。 - 前記直線状流入部の、前記一方の前記腕部に対する傾斜角は、前記熱交換器における各パスの熱負荷分布に応じて決められた角度である
ことを特徴とする請求項6記載の冷媒分配器。 - 前記第2の分配器は、
前記一方の前記腕部において前記直線状流入部と対向する壁面である衝突壁の並びに、内側に凹んだ窪みを有する
ことを特徴とする請求項2、請求項4~請求項7の何れか一項に記載の冷媒分配器。 - 前記第1の分配器はディストリビュータ又はヘッダで構成されることを特徴とする請求項1~請求項8の何れか一項に記載の冷媒分配器。
- 請求項1~請求項9の何れか一項に記載の冷媒分配器を用いたヒートポンプ装置。
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US14/761,366 US20150362222A1 (en) | 2013-01-22 | 2013-01-22 | Refrigerant distribution device and a heat pump apparatus using the same refrigerant distribution device |
JP2014558310A JP6278904B2 (ja) | 2013-01-22 | 2013-01-22 | 冷媒分配器及びこの冷媒分配器を用いたヒートポンプ装置 |
EP13873009.8A EP2955464A4 (en) | 2013-01-22 | 2013-01-22 | COOLANT DISTRIBUTOR AND HEAT PUMP DEVICE WITH COOLANT DISTRIBUTION |
PCT/JP2013/051146 WO2014115240A1 (ja) | 2013-01-22 | 2013-01-22 | 冷媒分配器及びこの冷媒分配器を用いたヒートポンプ装置 |
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Also Published As
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EP2955464A4 (en) | 2016-11-09 |
JPWO2014115240A1 (ja) | 2017-01-19 |
EP2955464A1 (en) | 2015-12-16 |
US20150362222A1 (en) | 2015-12-17 |
JP6278904B2 (ja) | 2018-02-14 |
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