EP1985949A1 - Wärmetauscher - Google Patents

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Publication number
EP1985949A1
EP1985949A1 EP07714290A EP07714290A EP1985949A1 EP 1985949 A1 EP1985949 A1 EP 1985949A1 EP 07714290 A EP07714290 A EP 07714290A EP 07714290 A EP07714290 A EP 07714290A EP 1985949 A1 EP1985949 A1 EP 1985949A1
Authority
EP
European Patent Office
Prior art keywords
heat exchange
header
exchange medium
tubes
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP07714290A
Other languages
English (en)
French (fr)
Inventor
Toru Moriya
Takahide Maezawa
Tadashi Nakabou
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Aircool Corp
Original Assignee
Denso Aircool Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Denso Aircool Corp filed Critical Denso Aircool Corp
Publication of EP1985949A1 publication Critical patent/EP1985949A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0011—Ejectors with the cooled primary flow at reduced or low pressure

Definitions

  • the present invention relates to a heat exchanger used in a freezer, refrigerator, or the like.
  • a heat exchanger In a heat exchanger, to increase the heat exchange efficiency, it is important to distribute a heat exchange medium that has been supplied to a header uniformly to a plurality of heat exchange tubes.
  • the heat exchange medium refrigerant
  • a heat exchanger equipped with a distributor where a plurality of distribution tubes are bent in three dimensions in respectively different forms is known, such as the conventional art disclosed by Japanese Laid-Open Patent Publication No. 2004-317056 .
  • This publication discloses a heat exchanger where a plurality of distribution tubes are collectively disposed in part of an entrance header where the liquid refrigerant accumulates.
  • the plurality of distribution tubes need to have different forms and to be bent into complex three-dimensional forms. This means that more parts are needed and the manufacturing cost tends to be higher. In addition, since space is required to dispose the distribution tubes that are bent in three dimensions, there tends to be an increase in the size of the header and the heat exchanger.
  • the heat exchanger disclosed in this publication is equipped with a refrigerant distributing means that uses flat distribution tubes, the flat distribution tubes are concentrated in one part of the header, and in particular the lower part of the header where a liquid refrigerant tends to accumulate, and the liquid refrigerant is caused to flow into a heat exchanger part.
  • the state of the refrigerant at the entry to the plurality of flat distribution tubes is close to uniform, but since there are differences in the pressure drop between tubes due to differences in the lengths of the tubes, the distribution of refrigerant to the plurality of tubes will not necessarily become uniform.
  • a plurality of flat distribution tubes with curved parts are disposed in this construction, a heat exchanger with a simple construction cannot be provided.
  • Japanese Laid-Open Patent Publication No. 2000-249428 discloses an evaporator including an entrance header, an exit header, and a plurality of tubes that extend between both headers, with a plurality of wavy fins being provided between adjacent tubes.
  • a plurality of refrigerant sprayers are provided at the entrance to the entrance header.
  • Each refrigerant sprayer has spray orifices.
  • spray orifices are provided at the entrance to the entrance header as in the evaporator disclosed in this document, it will still be difficult to spray the refrigerant uniformly into the entire header, with the sprayed amount and distribution tending to be affected by the flow rate.
  • a first aspect of the present invention is a heat exchanger that includes a plurality of tubes, an entrance header for distributing a heat exchange medium to the plurality of tubes, and an exit header for collecting the heat exchange medium from the plurality of tubes.
  • the entrance header of this heat exchanger includes a circulating conduit that is capable of circulating at least part of the heat exchange medium that has flowed into the entrance header.
  • the plurality of tubes are fluidly connected to at least part of the circulating conduit.
  • the entrance header also includes a mechanism (pressure difference generating mechanism) that sprays the heat exchange medium in an axial direction of the circulating conduit to generate a pressure difference that forcibly circulates at least part of the heat exchange medium that has flowed into the entrance header in the circulating conduit.
  • the state of the heat exchange medium inside the circulating conduit of the input header can be made more uniform or close to uniform. For example, even when a two-phase heat exchange medium including a gas phase and a liquid phase has flowed into the header, it is possible to suppress separation of the heat exchange medium into a liquid phase component and a gas phase component inside the entrance header.
  • this heat exchanger may omit distributer having pipes bent in complex three dimensions. It may also omit machining that bends tubes complexly to make the distribution of the heat exchange medium more uniform. Note that the present heat exchanger does not exclude devices that have pipes and tubes laid out in three dimensions or bent by machining in three dimensions. According to the present heat exchanger, it is possible to make the phase state and amount of the heat exchange medium distributed to the tubes uniform or close to uniform using a simpler construction. This means that a heat exchanger with favorable heat exchanging efficiency can be provided at comparatively low cost.
  • a pressure difference generating mechanism is driven by an external force such as a pump.
  • the heat exchange medium that flows into the heat exchanger is reduced in pressure or expanded in advance.
  • the heat exchanger since a new driving source is not required aside from a driving source typically used in a heat exchanger, the heat exchanger is economical. That is, the pressure difference generating mechanism should preferably be driven by the heat exchange medium flowing into the entrance header.
  • the pressure difference generating mechanism it is possible to use a construction such as a supercharger (a construction that resembles a supercharger) that rotates a turbine using the pressure of a driving part and forcibly draws in the heat exchange medium using a pressure difference generating part (a pressurizing part) such as a coaxial compressor.
  • a supercharger a construction that resembles a supercharger
  • a pressure difference generating part a pressurizing part
  • a mechanism that draws at least part of the heat exchange medium that has already flowed into the entrance header using the heat exchange medium flowing into the entrance header and mixes and sprays out the heat exchange medium flowing into the entrance header and the heat exchange medium that has already flowed into the entrance header is preferable as the pressure difference generating mechanism.
  • This type of mechanism is an ejector, where there is a drop in pressure inside the nozzle when the heat exchange medium is sprayed out at high speed from the ejector nozzle (or orifice or throttle part).
  • This pressure drop draws at least part of the heat exchange medium (existing heat exchange medium) that has flowed into the entrance header and mixes a heat exchange medium that is flowing into the entrance header and at least part of the heat exchange medium that has flowed into the entrance header to forcibly circulate at least part of the heat exchange medium that has flowed into the entrance header via the circulating conduit.
  • the term "ejector” here includes a type that uses a pressure drop caused by spraying out the heat exchange medium from the nozzle to draw and mix the heat exchange medium already present in the entrance header.
  • At least part of the circulating conduit of the entrance header can be constructed by a double pipe or multi-hole pipe (a "multi-layer pipe” or “multi-channel pipe”).
  • the pressure difference generating mechanism should preferably be provided at one end of the double pipe or multi-layer pipe and the respective pipes of the double pipe or multilayer pipe should preferably be fluidly connected at the other end. By doing so, it is possible to use at least part of the double pipe or multi-hole pipe as the circulating conduit.
  • the pressure difference generating mechanism may be provided separately from the entrance header and/or the heat exchanger.
  • a heat exchanger that includes a plurality of tubes, an entrance header for distributing a heat exchange medium to the plurality of tubes, and an exit header for collecting the heat exchange medium from the plurality of tubes, wherein the entrance header includes a circulating conduit capable of circulating at least part of the heat exchange medium that has flowed into the entrance header, wherein the plurality of tubes are fluidly connected to at least part of the circulating conduit.
  • a header for distributing a heat exchange medium to a plurality of tubes is a plurality of tubes.
  • This header includes a circulating conduit capable of circulating at least part of the heat exchange medium that has flowed into the header, wherein the plurality of tubes are fluidly connected to at least part of the circulating conduit.
  • This header may also include a pressure difference generating mechanism that is driven by the heat exchange medium flowing into the header. This pressure difference generating mechanism should preferably spray out the heat exchange medium in the axial direction of the circulating conduit from the pressure difference generating mechanism. It is also preferable for the pressure difference generating mechanism to be an ejector that uses the heat exchange medium flowing into the header to draw out and mix at least part of the (existing) heat exchange medium that has already flowed into the header and spray out the heat exchange medium into the circulating conduit.
  • the present invention also includes a heat exchange system that includes a heat exchanger according to the one of the aspects of the present invention and an apparatus (medium supplying system) that supplies the heat exchange medium to the heat exchanger.
  • the meaning of the heat exchange system or system includes a cooling cycle or a freezing cycle and a freezer, refrigerator, air conditioner, storage device, showcase, or the like that includes such cycle.
  • One of favorable systems as a cooling cycle or freezing cycle includes the heat exchanger according to one of the aspects of the present invention as an evaporator, an apparatus that pressurizes the heat exchange medium collected from the evaporator, and a condenser that cools the pressurized heat exchange medium.
  • the ejector also functions as an expansion means that lowers the pressure of a pressurized heat exchange medium and supplies the heat exchange medium to the evaporator.
  • a heat exchanger where the entrance header includes a circulating conduit and an ejector for mixing at least part of the heat exchange medium that has already flowed into the entrance header using the heat exchange medium flowing into the entrance header and spraying the heat exchange medium into the circulating conduit is suited to a cycle and/or system that circulates a refrigerant as the heat exchange medium.
  • expansion means that lowers the pressure of the pressurized heat exchange medium and supplies the heat exchange medium to the evaporator may be included or may be omitted from the medium supplying system.
  • FIG. 1 shows a system 50 that includes a heat exchanger.
  • This system (heat exchange system) 50 may be an air conditioner, a freezer, or another type of system, and also includes a heat exchange cycle called a "refrigeration cycle” or “freezing cycle” and a system with such heat exchange cycle.
  • the system 50 is an air conditioner system
  • the system (heat exchange system) 50 will exchange heat between a liquid heat exchange medium (hereinafter "refrigerant") R and an external flow (for example, outside air) F.
  • refrigerant liquid heat exchange medium
  • F for example, outside air
  • the system 50 includes an evaporator 100 that cools the indoor air G by heat exchange with the refrigerant R and a condenser 200 that carries out heat exchange between the refrigerant R in a pressurized gas state and the external flow F to liquefy the refrigerant R.
  • the system 50 includes appliances such as a compressor 51 that pressurizes the refrigerant R, an accumulator 52 in which the refrigerant R temporarily accumulates, and an expansion valve 53 that allows the refrigerant R supplied to the evaporator 100 to expand.
  • the refrigerant R inside the evaporator 100 circulates so as to flow out from a refrigerant outlet of the evaporator 100, pass through the accumulator 52, the compressor 51, the condenser 200, and the expansion valve 53 and then flow back into the evaporator 100 from the refrigerant inlet of the evaporator 100.
  • FIG. 2 shows a heat exchanger 100a according to a first embodiment of the present invention.
  • This heat exchanger 100a can be used as the evaporator 100 of the system 50.
  • the heat exchanger 100a includes an entrance header 1 that includes a refrigerant inlet 6, an exit header 2 that includes a refrigerant outlet 5, and a heat exchanging part 20.
  • the entrance header 1 and the exit header 2 both extend in the up-down direction (vertical direction) and are disposed so as to be parallel to one another.
  • the heat exchanging part 20 exchanges heat between the refrigerant R and the air G or the like so as to cool the air G or the like.
  • the heat exchanging part 20 includes a plurality of tubes 4, which are disposed in parallel in the horizontal direction so as to fluidly connect the entrance header 1 and the exit header 2, and fins 3, which extend in the up-down direction so as to be perpendicular to the tubes 4.
  • a typical example of the tubes 4 are tubes that are circular in cross-section, but the tubes may be flat tubes that are flattened in cross-section, and may also be multi-hole tubes (multi-channeled flat tubes) where the inside of a tube is subdivided into a plurality of sections.
  • a typical example of the fins 3 is a plurality of plate-type fins that are disposed in parallel to one another and are attached with the tubes 4 passing therethrough.
  • the fins 3 may be corrugated fins that connect and undulate between the tubes 4 or may project outward from the tubes 4 in the form of fins or pins.
  • the entrance header 1 functions as a distributor for distributing the refrigerant R to the plurality of tubes 4 of the heat exchanging part 20.
  • the exit header 2 functions so as to collect the refrigerant R from the respective tubes 4.
  • Each tube 4 is fluidly connected to the entrance header 1 at one end and to the exit header 2 at the other end.
  • the heat exchange area provided by the tubes themselves can be increased, and by further providing the fins 3, the heat exchange area (i.e., the contact area) with the gas G or the like can be further increased, thereby improving the heat exchange efficiency.
  • fins may not be provided or the area occupied by the fins may be reduced.
  • the entrance header 1 includes a circulating conduit 10, which forcibly circulates at least part of the refrigerant R that has flowed into the entrance header 1, and a pressure difference generating mechanism 11.
  • the circulating conduit 10 includes a straight outward channel 10a and a substantially U-shaped return channel 10b that connects one end of the outward channel 10a to the other end.
  • the outward channel 10a guides the refrigerant R from the refrigerant inlet 6 at the one end thereof to the opposite end.
  • the return channel 10b conversely guides the refrigerant R to the refrigerant inlet 6 from the opposite end of the outward channel 10a. Accordingly, the circulating conduit 10 including the outward channel 10a and the return channel 10b can circulate at least part of the refrigerant (in-flowed or existing refrigerant) R that flows into the entrance header 1.
  • the pressure difference generating mechanism 11 is an ejector that includes a throttle part (throat part) 7 and a drawing part (inlet part) 8, and is provided near the refrigerant inlet 6 of the entrance header 1.
  • the return channel 10b of the circulating conduit 10 is provided so as to fluidly connect (i) the periphery of the inner end (i.e., the upper end) 15 that is the opposite end of the entrance header 1 to the refrigerant inlet 6 and (ii) the drawing part 8 of the pressure difference generating mechanism 11.
  • the pressure difference generating mechanism 11 is driven by the refrigerant (in-flowing refrigerant) R flowing into the entrance header 1, with at least part of the refrigerant R that has already flowed into the entrance header 1 (i.e., existing refrigerant R) being drawn out, mixed and ejected into the outward channel 10a.
  • the plurality of tubes 4 are fluidly connected to the outward channel 10a that is part of the circulating conduit 10. That is, the plurality of tubes 4 are fluidly connected at substantially equal intervals between (i) a drawing channel 9 where the return channel 10b branches off in the circulating conduit 10 and (ii) the pressure difference generating mechanism 11.
  • a two-phase refrigerant R in which gas phase and liquid phase are mixed are supplied via the refrigerant inlet 6 to the entrance header 1 and passes the throat part 7 of the drawing part 8.
  • the refrigerant R flows into the entrance header 1 at high speed via the throat part 7, there is a decrease in pressure inside the throat part 7. Due to this reduction in pressure, at least part of the (existing) refrigerant R that has flowed into the entrance header 1 is drawn through the drawing part 8 via the return channel 10b.
  • the refrigerant R that is flowing into the entrance header 1 and at least part of the refrigerant R that has already flowed into the entrance header 1 are mixed, and as shown by the arrow in FIG. 2 , the mixed refrigerant R is sprayed from the pressure difference generating mechanism 11 inside the entrance header 1 in the direction of the axis L of the circulating conduit 10. Next, at least part of such mixed refrigerant R returns to the drawing part 8 via the outward channel 10a and the return channel 10b and becomes the existing or in-flowed refrigerant.
  • the plurality of tubes 4 are connected at substantially equal intervals in a center part of the outward channel 10a in which the refrigerant R flows upward from the bottom.
  • Part of the refrigerant R is distributed from the entrance header 1 to the respective tubes 4 and the state of the refrigerant R distributed to the respective tubes 4 can be made uniform.
  • the state of the refrigerant R in the outward channel 10a includes a mixture of gas phase and liquid phase in a homogenized state, the amount of refrigerant R distributed to the respective tubes 4 is also made more uniform.
  • the refrigerant R that is uniformly distributed to the tubes 4 in this way is subjected to heat exchange with the air G via the plurality of tubes 4 and the plurality of fins 3, is outputted to the exit header 2, and flows out into the system 50 from the refrigerant outlet 5. Accordingly, the heat exchange load of the respective tubes 4 is made uniform, resulting in a heat exchanger 100a with favorable heat exchange efficiency.
  • there is no need to provide a plurality of distribution pipes bent into different shapes in two or three dimensions in order to uniformly distribute the refrigerant into the respective tubes and it is therefore possible to provide a heat exchanger with a simple and compact construction and favorable heat exchange efficiency at comparatively low cost. Since it is also possible to produce the respective tubes 4 with the same shape, it is possible to avoid the generation of differences in pressure drop between the respective tubes 4, which also improves the heat exchange efficiency.
  • the heat exchanger 100a it is possible to prevent separation into phases due to a head difference in the entrance header 1. This means that the orientation (layout) of the entrance header 1 of the heat exchanger 100a becomes freer.
  • the heat exchanger 100a may be used in a posture where the entrance header 1 is disposed horizontally and may be used in a posture where the entrance header 1 is disposed vertically.
  • the refrigerant R may flow in from the bottom of the entrance header 1 or may flow in from the top of the entrance header 1.
  • the heat exchanger 100a in a variety of postures including cases where the entrance header 1 is disposed diagonally, with it being possible to uniformly distribute the refrigerant R to the plurality of tubes 4 when the heat exchanger 100a is used in such postures.
  • a cooling system 50 that is equipped with the heat exchanger 100a can use a compact arrangement.
  • the heat exchanger 100a uses the pressure difference generating mechanism 11 that utilizes an ejector effect, it is not necessary to use a driving means that is typically used in a heat exchanger, for example, a driving means aside from the compressor 51.
  • the heat exchanger is therefore economical.
  • by assigning part of the pressure loss due to the expansion valve 53 to the ejector 11 that is a pressure difference generating mechanism it is possible to improve the heat exchange efficiency without negatively affecting the economy of the system 50. Also, if there is sufficient expansion (i.e., pressure loss) due to the ejector 11, it is possible to omit the expansion valve 53.
  • FIG. 3 shows a heat exchanger 100b according to a second embodiment of the present invention.
  • This heat exchanger 100b can also be used as the evaporator 100 of the heat exchange system 50 described above.
  • a plurality of tubes 4 are connected at substantially equal intervals to the return channel 10b of the circulating conduit 10 of the entrance header 1.
  • the state of the refrigerant R becomes substantially uniformly mixed phase in not only the outward channel 10a but also the return channel 10b. Accordingly, it is possible to distribute the refrigerant R substantially uniformly to the respective tubes 4 when the tubes 4 are fluidly connected to the return channel 10b.
  • the phase state of the refrigerant R mixed by suction tends to be more stable or uniform than at a position immediately after the throat part 7 of the ejector 11.
  • the tubes 4 are fluidly connected to the return channel 10b, the ejector 11 that includes the throat part 7 and the tubes 4 are separated. Accordingly, it is possible to distribute the refrigerant R with more stabilized phase state to the tubes 4.
  • FIG. 4 shows a heat exchanger 100c according to a third embodiment of the present invention.
  • This heat exchanger 100c can also be used as the evaporator 100 of the heat exchange system 50 described above.
  • the entrance header 1 includes a U-shaped tube that includes two straight parts, with such straight parts being fluidly connected at the open end of the U shape by the drawing channel 9.
  • the entrance header 1 includes a circulating conduit (circulating pathway) 10 and both the outward channel 10a and the return channel 10b of the circulating conduit 10 are fluidly connected to the plurality of tubes 4. Accordingly, it is possible to supply the refrigerant R in a substantially uniform state to the plurality of tubes 4 that are aligned in two columns along the outward channel 10a and the return channel 10b.
  • the heat exchanger 100c it is possible to further increase the heat exchange efficiency of the heat exchanging part 20 without changing the surface area (projected area) of the heat exchanging part 20 on a plane.
  • FIG. 5 shows a heat exchanger 100d according to a fourth embodiment of the present invention.
  • This heat exchanger 100d includes two heat exchangers 20a and 20b and can be used as the evaporator 100 of the heat exchange system 50 described above.
  • This heat exchanger 100d is provided with an entrance header 1 that is shared by or common to the heat exchangers 20a and 20b, the plurality of tubes 4 of one of the heat exchangers (the heat exchanging part 20a) are connected to the outward channel 10a of the circulating conduit 10 of the header 1, and the plurality of tubes 4 of the other heat exchanger (the heat exchanging part 20b) are connected to the return channel 10b.
  • the refrigerant R can be equally distributed to the tubes 4 of a plurality of heat exchanger parts 20a and 20b using a single entrance header 1.
  • the number of heat exchanger parts that can be connected to a single entrance header may be three or higher.
  • FIG. 6 shows a heat exchanger 100e according to a fifth embodiment of the present invention.
  • This heat exchanger 100e can also be used as the evaporator 100 of the heat exchange system 50 described above.
  • the entrance header 1 of this heat exchanger 100e includes a double pipe 12 and the pressure difference generating mechanism (ejector) 11 is provided at the bottom end of the double pipe 12.
  • An inner pipe 12a and the outer pipe 12b of the double pipe 12 are fluidly connected to one another at the upper end of the double pipe 12.
  • the ejector 11 is installed so as to eject the refrigerant R in the axial direction of the inner pipe 12a located on the inside of the double pipe 12.
  • the inner pipe 12a of the double pipe 12 constructs the outward channel and the outer pipe 12b forms the return channel, with the circulating conduit 10 being constructed of these channels.
  • the plurality of tubes 4 are fluidly connected to the outer pipe 12 that is the return channel.
  • the circulating conduit 10 since the circulating conduit 10 is included in the inside of a single pipe, it is possible to provide a heat exchanger that is even more compact and has a simple external appearance.
  • the circulating conduit 10 integrating like a single pipe is not limited to a double pipe and it is possible to use a multi-channel pipe (a multi-hole pipe) where a suitable number of partitions are provided on the inside of the pipe.
  • FIG. 7 shows a different example of the pressure difference generating mechanism 11.
  • the pressure difference generating mechanism 11 in the respective embodiments described above is an ejector where the drawing part 8 is provided at the throttle or throat part 7 of a venturi tube.
  • the pressure difference generating mechanism 11 shown in FIG. 7 is an atomizer-type ejector.
  • the pressure difference generating mechanism 11 includes a suction nozzle 17 provided on the refrigerant inlet 6 of the header 1 for producing a pressure difference and lowering the pressure by the refrigerant flowing in to draw the existing or in-flowed refrigerant R that has flowed into the header 1 and to spray the refrigerant R mixed of in-flowing and in-flowed in the axial direction of the circulating conduit.
  • a suction hole 18 for drawing the existing refrigerant R that has already flowed into the header 1 from the return channel 10b is provided in the periphery of the suction nozzle 17 of the outward channel 10a. Due to the pressure drop caused by the refrigerant R flowing in and spraying out from the suction nozzle 17, the refrigerant R that has flowed into the header 1 is drawn into the outward channel 10a and is going out with the sprayed one in the axial direction of the outward channel 10a. The refrigerant R is forcibly circulated in the circulating conduit 10 that constructs the entrance header 1 by the pressure difference generating mechanism 11.
  • FIG. 8, FIG. 9 , and FIG. 10 show the construction of a heat exchanger 100f, focusing on the periphery of the entrance header 1, according to a sixth embodiment of the present invention.
  • This heat exchanger 100f can also be used as the evaporator 100 of the heat exchange system 50 described above.
  • the entrance header 1 of the heat exchanger 100f includes a double pipe 12 that includes an inner pipe 12a and an outer pipe 12b, with the inner pipe 12a and the outer pipe 12b being fluidly connected at the top part of the header 1.
  • the outer pipe 12b is composed of two members 13a and 13b that are semicircular in cross-section and are formed by extrusion and machining.
  • a plurality of flat tubes 14 are attached to the inside (exchanger side) member 13b and these flat tubes 14 are connected to an exit header (not shown).
  • the inner pipe 12a is constructed by attaching a member 15 that is semicircular in cross section to the outside member 13a. Both ends of the two members 13a and 13b that construct the outer pipe 12b are covered by caps 16.
  • the nozzle 17 is attached to the bottom end of the inner pipe 12a and sprays the refrigerant R flowing into the header 1 inside the inner pipe 12a.
  • This nozzle 17 forms the pressure difference generating mechanism 11, and due to the spray force of the refrigerant R sprayed out from the bottom toward the top of the inner pipe 12a, the existing refrigerant R (that has already flowed in) is drawn into the inner pipe 12a from the outer pipe 12b via the gap 18 at the bottom of the inner pipe 12a.
  • the header 1 is equipped with the circulating conduit 10 that includes the inner pipe 12a and the outer pipe 12b and is connected to the tubes 14, and the refrigerant R is forcibly circulated in the circulating conduit 10. It is possible to provide a heat exchanger with high heat exchange efficiency where the state of the refrigerant R inside the header 1 can be made more uniform.
  • heat exchangers that are used in a posture where the headers are disposed vertically are described above in the first to sixth embodiments, it is also possible to use the heat exchangers in a posture where the headers are disposed horizontally.
  • the first to sixth embodiments described above include a circulating means equipped with a pressure difference generating mechanism driven by the heat exchange medium that flows into the header and a circulating conduit for circulating at least part of the heat exchange medium that has flowed into the header
  • the circulating means is not limited to this. Any type of circulating means to forcibly circulate part of the existing or in-flowed heat exchange medium (i.e., refrigerant) that has flowed into the header is applicable.
  • a pressure difference generating mechanism equipped with an ejector nozzle is a favorable example of the present invention, and by providing such mechanism in the periphery of the refrigerant inlet of the header, it is possible to draw and mix at least part of the refrigerant that has flowed into the entrance header using the refrigerant that is flowing into the entrance header and spray out the refrigerant that has been mixed into the header. Accordingly, this is suited to a cycle where the inner pressure of the heat exchanger is set low and the refrigerant is circulated as described above, and to a system that includes such cycle.
  • a pressure difference generating mechanism driven by refrigerant that has flowed into the header is a supercharger that rotates a turbine using the pressure of a driving part and forcibly draws the heat exchange medium using a pressure difference generating part (a pressurizing part) such as a coaxial compressor.
  • a pressure difference generating part such as a pressurizing part
  • the driving part and the pressure difference generating part are separated and are mechanically connected.
  • a pressure difference generating mechanism such as a pump that is driven by a separate driving force. That is, the pressure difference generating mechanism may be a mechanism that pumps the refrigerant circulating inside the entrance header without mixing such refrigerant with the refrigerant flowing into the entrance header.
  • a pressure difference generating mechanism like a pump forcibly circulates the existing refrigerant inside the entrance header by pressurizing the existing refrigerant, such pressure difference generating mechanism does not need to be provided near the refrigerant inlet of the header.
  • This type of pressure difference generating mechanism may be provided midway in the circulating conduit, for example, in a conduit, out of the outward channel and the return channel, that is not connected to the header, in a connecting path that connects such for such channels, or the like. It is also possible to use a mechanism that can detachably attach the pressure difference generating mechanism to the circulating conduit of the header.
  • conduits that function as the outward channel and the return channel and a suitable pressure difference generating mechanism in a header of a type where refrigerant is not circulated, it is possible to construct a heat exchanger or a heat exchange system that is similar to the embodiments of the present invention.
  • heat exchangers where the heat exchanger part is equipped with plate-type fins have been described in the above embodiments, the shape of the fins is not limited to plate-like shapes. Also, the heat exchanger part only needs to be able to carry out heat exchange between the refrigerant (heat exchange medium) and an external flow such as air, and the form and construction of the heat exchanger part are not limited to the examples above.
  • system according to the present invention is not limited to air conditioning and applicable to apparatuses and systems that include any out of a variety of heat exchanging functions, such as a radiator, various types of cooling apparatuses, and various types of freezers.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
EP07714290A 2006-02-15 2007-02-15 Wärmetauscher Withdrawn EP1985949A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006037791 2006-02-15
PCT/JP2007/052760 WO2007094422A1 (ja) 2006-02-15 2007-02-15 熱交換器

Publications (1)

Publication Number Publication Date
EP1985949A1 true EP1985949A1 (de) 2008-10-29

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3081985A1 (fr) * 2018-05-31 2019-12-06 Valeo Systemes Thermiques Distributeur de fluide, et echangeur thermique correspondant.
EP3855059B1 (de) * 2020-01-24 2023-11-15 Aptiv Technologies Limited Passiver strömungsteiler und flüssigkeitskühlsystem damit

Families Citing this family (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009150574A (ja) * 2007-12-19 2009-07-09 Mitsubishi Electric Corp 分配器、およびそれを搭載した熱交換器並びに空気調和機
CN201488380U (zh) * 2009-09-16 2010-05-26 倪军 用于制冷设备中的恒压衡功制冷系统装置
CN102470729A (zh) * 2009-10-13 2012-05-23 昭和电工株式会社 中间热交换器
JP5567935B2 (ja) * 2010-08-19 2014-08-06 日立アプライアンス株式会社 冷媒分配器及び冷凍サイクル装置
JP5763436B2 (ja) * 2011-06-20 2015-08-12 シャープ株式会社 パラレルフロー型熱交換器及びそれを搭載した空気調和機
CN103148729B (zh) * 2013-03-19 2015-01-21 丹佛斯微通道换热器（嘉兴）有限公司 集流管以及具有集流管的换热器
CN103206885B (zh) * 2013-03-27 2015-06-03 美的集团股份有限公司 集流管、平行流换热器及空调装置
US9670937B2 (en) * 2013-05-30 2017-06-06 Ingersoll-Rand Company Centrifugal compressor having cooling system
US9989283B2 (en) 2013-08-12 2018-06-05 Carrier Corporation Heat exchanger and flow distributor
JP5741658B2 (ja) * 2013-09-11 2015-07-01 ダイキン工業株式会社 熱交換器及び空気調和機
JP5754490B2 (ja) * 2013-09-30 2015-07-29 ダイキン工業株式会社 熱交換器および空気調和装置
JP6179399B2 (ja) * 2013-12-27 2017-08-16 ダイキン工業株式会社 熱交換器および空気調和装置
JP5741680B1 (ja) * 2013-12-27 2015-07-01 ダイキン工業株式会社 熱交換器および空気調和装置
JP5794293B2 (ja) * 2013-12-27 2015-10-14 ダイキン工業株式会社 熱交換器および空気調和装置
JP6188951B2 (ja) * 2014-07-31 2017-08-30 三菱電機株式会社 冷媒分配器、熱交換器および冷凍サイクル装置
US10197312B2 (en) * 2014-08-26 2019-02-05 Mahle International Gmbh Heat exchanger with reduced length distributor tube
JP5850118B1 (ja) * 2014-09-30 2016-02-03 ダイキン工業株式会社 熱交換器および空気調和装置
JP6070685B2 (ja) * 2014-12-26 2017-02-01 ダイキン工業株式会社 熱交換器および空気調和装置
JP6458680B2 (ja) * 2015-02-02 2019-01-30 株式会社デンソー 熱交換器
JP2016148480A (ja) * 2015-02-12 2016-08-18 株式会社デンソー 熱交換器
EP3370020B1 (de) * 2015-10-26 2020-07-01 Mitsubishi Electric Corporation Kältemittelverteiler und klimaanlage damit
JP2019207033A (ja) * 2016-09-28 2019-12-05 東芝キヤリア株式会社 熱交換器および冷凍サイクル装置
US11181328B2 (en) 2017-03-27 2021-11-23 Daikin Industries, Ltd. Heat exchanger and air conditioner
JP6369648B1 (ja) * 2017-03-27 2018-08-08 ダイキン工業株式会社 熱交換器および空気調和装置
EP3605001B1 (de) * 2017-03-29 2024-05-01 Daikin Industries, Ltd. Wärmetauscher
JP7086264B2 (ja) * 2018-10-29 2022-06-17 三菱電機株式会社 熱交換器、室外機、及び冷凍サイクル装置
EP3875878B1 (de) * 2018-10-29 2022-06-08 Mitsubishi Electric Corporation Wärmetauscher und kühlzyklusvorrichtung
CN110567196A (zh) * 2019-09-10 2019-12-13 江苏科菱库精工科技有限公司 一种微通道换热器的制冷剂分配装置及使用方法
CN114623702B (zh) * 2020-12-11 2023-08-29 杭州三花微通道换热器有限公司 换热器
US20240060722A1 (en) * 2021-02-26 2024-02-22 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2097602A (en) * 1936-03-06 1937-11-02 Warren Webster & Co Radiator
US2088609A (en) * 1936-07-28 1937-08-03 Randel Bo Folke Method of and apparatus for refrigerating
US2766740A (en) * 1955-03-07 1956-10-16 Adolph A Tacchella Cooling system for internal combustion engines
US2825317A (en) * 1956-01-09 1958-03-04 Adolph A Tacchella Steam separator
DE3413931A1 (de) * 1984-04-13 1985-10-24 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co. KG, 7000 Stuttgart Verdampfer, insbesondere fuer klimaanlagen in kraftfahrzeugen
JPH06127695A (ja) * 1991-07-15 1994-05-10 Kanebo Ltd カップ切出し装置
JPH0790251B2 (ja) * 1991-09-25 1995-10-04 川崎製鉄株式会社 スプレーヘッダ及びこれを用いた圧延油供給装置
JP3265649B2 (ja) * 1992-10-22 2002-03-11 株式会社デンソー 冷凍サイクル
JPH0910817A (ja) * 1995-06-27 1997-01-14 Kawasaki Steel Corp 圧延油のスプレーヘッダおよびその使用方法
US5910167A (en) 1997-10-20 1999-06-08 Modine Manufacturing Co. Inlet for an evaporator
JPH11337293A (ja) * 1998-05-26 1999-12-10 Showa Alum Corp 蒸発器
US6688137B1 (en) * 2002-10-23 2004-02-10 Carrier Corporation Plate heat exchanger with a two-phase flow distributor
JP2004232924A (ja) * 2003-01-29 2004-08-19 Denso Corp 冷凍サイクル装置
JP3818270B2 (ja) 2003-04-17 2006-09-06 株式会社デンソー 熱交換器
JP4259478B2 (ja) * 2004-02-18 2009-04-30 株式会社デンソー 蒸発器構造およびエジェクタサイクル
US20050262872A1 (en) * 2004-05-26 2005-12-01 Carrier Corporation Two-phase refrigerant distribution system for parallel tube evaporator coils
US7331195B2 (en) * 2004-10-01 2008-02-19 Advanced Heat Transfer Llc Refrigerant distribution device and method

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007094422A1 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3081985A1 (fr) * 2018-05-31 2019-12-06 Valeo Systemes Thermiques Distributeur de fluide, et echangeur thermique correspondant.
EP3855059B1 (de) * 2020-01-24 2023-11-15 Aptiv Technologies Limited Passiver strömungsteiler und flüssigkeitskühlsystem damit

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JP4866416B2 (ja) 2012-02-01
JPWO2007094422A1 (ja) 2009-07-09
CN101384868A (zh) 2009-03-11
WO2007094422A1 (ja) 2007-08-23

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