EP2602578B1 - Échangeur de chaleur et dispositif de conditionnement d'air et de réfrigération - Google Patents

Échangeur de chaleur et dispositif de conditionnement d'air et de réfrigération Download PDF

Info

Publication number
EP2602578B1
EP2602578B1 EP11814315.5A EP11814315A EP2602578B1 EP 2602578 B1 EP2602578 B1 EP 2602578B1 EP 11814315 A EP11814315 A EP 11814315A EP 2602578 B1 EP2602578 B1 EP 2602578B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
temperature fluid
low
flat pipes
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.)
Active
Application number
EP11814315.5A
Other languages
German (de)
English (en)
Other versions
EP2602578A4 (fr
EP2602578A1 (fr
Inventor
Susumu Yoshimura
Hiroaki Nakamune
Mizuo Sakai
Soshi Ikeda
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric 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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP2602578A1 publication Critical patent/EP2602578A1/fr
Publication of EP2602578A4 publication Critical patent/EP2602578A4/fr
Application granted granted Critical
Publication of EP2602578B1 publication Critical patent/EP2602578B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F7/00—Elements not covered by group F28F1/00, F28F3/00 or F28F5/00
    • F28F7/02—Blocks traversed by passages for heat-exchange media
    • 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
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the present invention relates to a heat exchanger that is adapted to exchange heat between a low-temperature fluid and a high-temperature fluid so as to transfer the heat from the high-temperature fluid to the low-temperature fluid. Moreover, the present invention relates to a refrigeration and air-conditioning apparatus equipped with such a heat exchanger.
  • a heat exchanger in the related art includes a first passage section having a plurality of through-holes through which a low-temperature fluid flows, a second passage section having a plurality of through-holes through which a high-temperature fluid flows, first headers connected to both ends of the first passage section, and second headers connected to both ends of the second passage section.
  • the first passage section and the second passage section are stacked with surfaces thereof in contact with each other such that longitudinal directions (i.e., fluid flowing directions) thereof are parallel to each other.
  • at least one of the high-temperature fluid and the low-temperature fluid is a fluid in a two-phase gas-liquid state.
  • An inlet header through which the fluid in the two-phase gas-liquid state flows has an inner diameter that is smaller than the inner diameter of the other headers.
  • the gas and the liquid are made uniform by mixing of the gas and the liquid within a pipe due to an increase in gas flow velocity, so that the low-temperature fluid is distributed to the through-holes with a uniform gas-to-liquid ratio, thereby maximizing the temperature efficiency of the fluid and achieving high heat exchanging performance (for example, see Patent Literature 1).
  • Patent Literature 2 discloses a heat exchanger that realizes both ensuring of heat exchange performance and reduction of the longitudinal dimension.
  • Patent Literature 3 discloses a heat exchanging structure that is high in heat efficiency and is suited for temporarily heating various fluids.
  • a refrigeration and air-conditioning apparatus that uses the aforementioned heat exchanger in the related art has a refrigerant circuit in which a compressor, a radiator, flow control means, and an evaporator are connected by a refrigerant pipe, and a refrigerant, such as an HFC (hydrofluorocarbon) based refrigerant, hydrocarbon, or carbon dioxide, circulates through this refrigerant circuit.
  • a refrigerant such as an HFC (hydrofluorocarbon) based refrigerant, hydrocarbon, or carbon dioxide
  • the present invention has been made to solve the aforementioned problems, and an object thereof is to obtain a compact, high-performance heat exchanger and a compact, high-performance refrigeration and air-conditioning apparatus.
  • a refrigeration and air-conditioning apparatus according to the present invention is equipped with the heat exchanger according to the present invention.
  • a compact, high-performance heat exchanger can be provided. Furthermore, according to the present invention, a compact, high-performance refrigeration and air-conditioning apparatus can be provided.
  • FIG. 1 illustrates a heat exchanger according to Example 1 which is outside the scope of the claimed invention, and includes FIG. 1(a) showing a perspective view, FIG. 1(b) showing a side view, and FIG. 1(c) showing a sectional view of the vicinity of a connection area between a second inlet header and each second flat pipe.
  • FH shown in FIG. 1(a) denotes the flow of a high-temperature fluid
  • FC shown in FIG. 1(a) denotes the flow of a low-temperature fluid.
  • Example 1 is directed to a case where the low-temperature fluid in a two-phase gas-liquid state flows into the second header.
  • components given the same reference numerals or characters indicate the same components or equivalent components, and this commonly applies throughout the entire specification.
  • Example 1 a substantially-horizontal inflow segment 2a is provided at an end of each second flat pipe 2 shown in FIG. 1 on the basis of information obtained from tests shown in FIGs. 3 to 5 , that is, the ranges of position angles ⁇ , ⁇ , and ⁇ , to be described later, providing excellent heat transfer characteristics, whereby a heat exchanger 10 having excellent heat transfer characteristics is achieved.
  • the second flat pipes 2 are connected to a second inlet header 5 with a position angle ⁇ of 90°.
  • First flat pipes 1 each have a plurality of through-holes extending in the longitudinal direction (i.e., the left-right direction in FIG. 1(b) ) and through which the high-temperature fluid flows.
  • the through-holes are arranged parallel to each other in the width direction of the first flat pipe 1 (i.e., a direction orthogonal to the plane of FIG. 1(b) ).
  • the second flat pipes 2 each have a plurality of through-holes 21 extending in the longitudinal direction (i.e., the left-right direction in FIG. 1(b) ) and through which the low-temperature fluid flows.
  • the through-holes 21 are arranged parallel to each other in the width direction of the second flat pipe 2 (i.e., the direction orthogonal to the plane of FIG. 1(b) ).
  • the first flat pipes 1 and the second flat pipes 2 are stacked such that flat surfaces of the first flat pipes 1 and flat surfaces of heat exchanging segments 2c of the second flat pipes 2 are in contact with each other.
  • first flat pipes 1 and the second flat pipes 2 are stacked such that the flowing directions of the fluids flowing through the flat pipes 1 and 2 are parallel to each other.
  • the first flat pipes 1 and the second flat pipes 2 are joined to each other by, for example, soldering or bonding.
  • soldering or bonding For example, if the first flat pipes 1 and the second flat pipes 2 are both composed of aluminum or an aluminum alloy, the solder or flux used for soldering is composed of aluminum/silicon-based material, fluoride-based material, or the like.
  • the solder or flux used for soldering is composed of zinc/aluminum-based material, aluminum/cesium/fluoride-based material or the like.
  • a combination of solder and flux a combination in which the melting point of the former is close to the activation temperature of the latter is preferable since the solderability improves due to, for example, better flowability of the solder.
  • each first flat pipe 1 is connected to a side surface of a first inlet header 3 having a tubular shape, while the other end is connected to a side surface of a first outlet header 4 having a tubular shape.
  • the through-holes formed in the first flat pipes 1 form parallel passages through which the high-temperature fluid flows.
  • the inflow segment 2a serving as one longitudinal end of each second flat pipe 2 is connected to a side surface of the second inlet header 5 having a tubular shape.
  • An outflow segment 2d serving as the other longitudinal end of each second flat pipe 2 is connected to a side surface of a second outlet header 6 having a tubular shape.
  • the inflow segment 2a and the outflow segment 2d are connected to the heat exchanging segment 2c via bent segments 2b.
  • the through-holes 21 formed in the second flat pipes 2 form parallel passages through which the low-temperature fluid flows.
  • the first inlet header 3, the first outlet header 4, the second inlet header 5, and the second outlet header 6 are disposed such that axial directions thereof are parallel to the flat surfaces of the flat pipes 1 and 2 (specifically, the parallel-arranged direction of the through-holes formed in the flat pipes 1 and 2).
  • the inflow segments 2a of the second flat pipes 2, through which the low-temperature fluid in the two-phase gas-liquid state flows, connected to the second inlet header 5 are substantially horizontal.
  • the passages (in other words, the through-holes 21 in the inflow segments 2a) for the low-temperature fluid in the two-phase gas-liquid state flowing into the second flat pipes 2 from the second inlet header 5 are substantially horizontal.
  • the first flat pipes 1 correspond to a "first passage section” according to the present invention
  • the second flat pipes 2 correspond to a "second passage section” according to the present invention.
  • the high-temperature fluid flows through the first inlet header 3, the first flat pipes 1, and the first outlet header 4 in that order
  • the low-temperature fluid flows through the second inlet header 5, the second flat pipes 2, and the second outlet header 6 in that order, and the two fluids exchange heat via contact sections between the first flat pipes 1 and the second flat pipes 2 (more specifically, the heat exchanging segments 2c).
  • the high-temperature fluid flowing through the through-holes in the first flat pipes 1 and the low-temperature fluid flowing through the through-holes in the second flat pipes 2 exchange heat via outer hulls, serving as partition walls between the through-holes, of the first flat pipes 1 and the second flat pipes 2.
  • the heat exchanger 10 is constituted of several first flat pipes 1 and several second flat pipes 2 in Example 1, the number of flat pipes 1 and the number of flat pipes 2 are not limited to the numbers in Example 1.
  • the parallel passages may be formed by alternately arranging one first flat pipe 1 and one second flat pipe 2 along a flat plane.
  • first flat pipes 1 and the second flat pipes 2 in Example 1 are disposed in contact with each other such that the flowing directions of the fluids flowing therethrough are parallel to each other, the flat pipes may alternatively be disposed in contact with each other such that the flowing directions are orthogonal to each other.
  • first flat pipes 1 and the second flat pipes 2 may be stacked while folding the first flat pipes 1 and the second flat pipes 2. Furthermore, although the end of the inflow segment 2a of each second flat pipe 2 is substantially aligned with the inner surface of the second inlet header 5 in FIG. 1(c) , the end of the inflow segment 2a of each second flat pipe 2 may alternatively protrude into the second inlet header 5.
  • the ends of the second flat pipes 2, through which the two-phase gas-liquid fluid flows, connected to the second inlet header 5 are substantially horizontal.
  • the outflowing direction of the two-phase gas-liquid fluid flowing out from the second inlet header 5 toward the through-holes 21 is substantially horizontal.
  • Example 1 even when the refrigerant flow velocity within the second inlet header 5 decreases to cause the gas and the liquid to flow separately through the upper side and the lower side therein, the liquid accumulates from the bottom of the second inlet header 5 to near the inflow segments of the second flat pipes 2 so that a gas-liquid interface is formed exactly near the inflow segments of the second flat pipes 2, whereby favorable gas-liquid distribution is achieved.
  • the low-temperature fluid can be distributed to the through-holes 21 in the second flat pipes 2 with a uniform gas-to-liquid ratio so that the temperature efficiency of the fluid can be maximized and the pressure loss can be minimized, thereby allowing for improved heat exchanging performance of the heat exchanger 10. Consequently, with the heat exchanger 10 according to Example 1, a compact, high-performance heat exchanger can be obtained.
  • the ends of the flat pipes connected to the remaining headers 3, 4, and 6 do not particularly need to be horizontal unless a two-phase gas-liquid fluid flows therethrough.
  • the inflow segments 2a are formed by bending the second flat pipes 2 outside the second inlet header 5 in Example 1, the inflow segments 2a may alternatively be formed by bending the second flat pipes 2 inside the second inlet header 5 to an extent that the gas-liquid flow within the second inlet header 5 is not disturbed, as shown in FIG. 2 .
  • the inflow segments 2a of the second flat pipes 2 connected to the second inlet header 5 are maintained in a substantially horizontal state even if the heat exchanger 10 is positionally inverted. Therefore, the gas-liquid distribution does not deteriorate. Consequently, the heat exchanger 10 according to Example 1 is advantageous in that the degree of freedom in terms of installation and the degree of freedom in terms of connection and routing of pipes are increased.
  • the distribution characteristics of the two-phase gas-liquid fluid toward the through-holes in the flat pipes change significantly depending on the outflowing direction of the fluid flowing out from the header toward the through-holes (in other words, the inflowing direction of the fluid flowing into the through-holes). Therefore, an effect that this direction has on the heat transfer characteristics (i.e., the distribution characteristics of the two-phase gas-liquid fluid) in the heat exchanger 10 is examined by performing tests ( FIGs. 3 to 5 ).
  • the mass flow rate M h of the high-temperature fluid is 600 kg/h.
  • a mass flow rate M c of the low-temperature fluid ranges between 80 kg/h and 100 kg/h.
  • a ratio of the mass flow rate of the gas to the overall mass flow rate of the gas and the liquid in the low-temperature fluid i.e., quality X
  • This range of the quality X is a generally used range for the inlet quality in the heat exchanger 10 used in a common refrigeration and air-conditioning apparatus.
  • the triangles, squares, and circles shown in FIG. 3(c) , FIG. 4(c) , and FIG. 5(c) express the heat transfer characteristics under the following conditions.
  • the squares express the heat transfer characteristics when the mass flow rate M c of the low-temperature fluid is 80 kg/h.
  • the triangles express the heat transfer characteristics when the mass flow rate M c of the low-temperature fluid is 90 kg/h.
  • the circles express the heat transfer characteristics when the mass flow rate M c of the low-temperature fluid is 100 kg/h.
  • FIG. 3 illustrates the heat transfer characteristics obtained when the second inlet header 5 is horizontally disposed and the position angle ⁇ , which corresponds to the outflowing direction of the low-temperature fluid in the two-phase gas-liquid state flowing out toward the through-holes 21 in the second flat pipes 2 (in other words, the inflowing direction of the low-temperature fluid flowing into the through-holes 21), is changed.
  • FIG. 3(a) is a diagram for explaining the position angle ⁇ .
  • FIG. 3(b) illustrates the positions of the heat exchanger 10 at main position angles ⁇ .
  • FIG. 3(c) shows a test result and illustrates the relationship between the position angle ⁇ and the heat transfer characteristics (relative value).
  • the heat transfer characteristics (relative value) of the heat exchanger 10 indicated on the ordinate axis in FIG. 3(c) are expressed by relative values, with 1 as the heat transfer characteristics obtained under a condition in which the low-temperature fluid is distributed to the through-holes 21 in the second flat pipes 2 with a uniform gas-to-liquid ratio.
  • the ends of the second flat pipes 2 shown in FIG. 3 each have one folded section.
  • the inflow segment 2a and the outflow segment 2d are directly connected to the heat exchanging segment 2c (without the intervention of the bent segments 2b).
  • the position angle ⁇ 0°, the low-temperature fluid (in the two-phase gas-liquid state) flows out toward the through-holes 21 in the second flat pipes 2 in a vertically upward direction.
  • the position angle ⁇ is set to substantially -90° or substantially 90°, even when the flow velocity within the second inlet header 5 decreases to cause the gas and the liquid to flow separately through the upper side and the lower side therein, the inflow segments extending from the second inlet header 5 to the second flat pipes 2 are prevented from being constantly filled with the liquid, thereby preventing deterioration in the gas-liquid distribution caused by the liquid alone flowing out selectively to the second flat pipes 2 located at the upstream side.
  • the liquid tends to flow into the second flat pipes 2 located toward the far side as viewed from the inlet side of the second inlet header 5 due to, for example, inertia of the liquid.
  • the flow is suppressed by gravity acting on the liquid, deterioration in the distribution is minimized to a certain extent.
  • FIG. 4 illustrates the heat transfer characteristics obtained when the outflowing direction of the low-temperature fluid in the two-phase gas-liquid state flowing out toward the through-holes 21 in the second flat pipes 2 is set to be horizontal and the position angle ⁇ of the second inlet header 5 is changed.
  • FIG. 4(a) is a diagram for explaining the position angle ⁇ .
  • FIG. 4(b) illustrates the positions of the heat exchanger 10 at main position angles ⁇ .
  • FIG. 4(c) shows a test result and illustrates the relationship between the position angle ⁇ and the heat transfer characteristics (relative value).
  • the heat transfer characteristics (relative value) of the heat exchanger 10 indicated on the ordinate axis in FIG. 4(c) are expressed by relative values, with 1 as the heat transfer characteristics obtained under a condition in which the low-temperature fluid is distributed to the through-holes 21 in the second flat pipes 2 with a uniform gas-to-liquid ratio.
  • the ends of the second flat pipes 2 shown in FIG. 4 do not have folded sections.
  • FIG. 5 illustrates the heat transfer characteristics obtained when both the position of the second inlet header 5 and the outflowing direction of the low-temperature fluid in the two-phase gas-liquid state flowing out toward the through-holes 21 in the second flat pipes 2 are changed.
  • FIG. 5(a) is a diagram for explaining the position angle ⁇ .
  • FIG. 5(b) illustrates the positions of the heat exchanger 10 at main position angles ⁇ .
  • FIG. 5(c) shows a test result and illustrates the relationship between the position angle ⁇ and the heat transfer characteristics (relative value).
  • the heat transfer characteristics (relative value) of the heat exchanger 10 indicated on the ordinate axis in FIG. 5(c) are expressed by relative values, with 1 as the heat transfer characteristics obtained under a condition in which the low-temperature fluid is distributed to the through-holes 21 in the second flat pipes 2 with a uniform gas-to-liquid ratio.
  • the ends of the second flat pipes 2 shown in FIG. 5 each have one folded section.
  • the inflow segment 2a and the outflow segment 2d are directly connected to the heat exchanging segment 2c (without the intervention of the bent segments 2b).
  • the low-temperature fluid (in the two-phase gas-liquid state) flows out toward the through-holes 21 in the second flat pipes 2 in the vertically upward direction, and the low-temperature fluid (in the two-phase gas-liquid state) flows into the second inlet header 5 in the horizontal direction.
  • 90° ⁇ position angle ⁇ ⁇ 180° the low-temperature fluid (in the two-phase gas-liquid state) flows out toward the through-holes 21 in the second flat pipes 2 upward relative to the horizontal direction, and the low-temperature fluid (in the two-phase gas-liquid state) flows into the second inlet header 5 upward relative to the horizontal direction.
  • At least one of the high-temperature fluid flowing into the through-holes in the first flat pipes 1 from the first inlet header 3 and the low-temperature fluid flowing into the through-holes 21 in the second flat pipes 2 from the second inlet header 4 is a fluid in a two-phase gas-liquid state.
  • the two-phase gas-liquid fluid flows into the flat pipes from the inlet header in a substantially horizontal direction or in an upward direction relative to the substantially horizontal direction.
  • the inflow segments extending from the second inlet header 5 to the second flat pipes 2 are prevented from being constantly filled with the liquid, thereby preventing deterioration in the gas-liquid distribution caused by the liquid alone flowing out selectively to the second flat pipes 2 located at the upstream side. Therefore, the two-phase gas-liquid fluid can be distributed to the through-holes with a uniform gas-to-liquid ratio so that the temperature efficiency of the fluid can be maximized and the pressure loss can be minimized. In other words, the heat exchanging performance of the heat exchanger 10 can be improved.
  • Example 1 The description of Example 1 is directed to a case where the low-temperature fluid flowing through the second inlet header 5 turns into a two-phase gas-liquid state. If the high-temperature fluid flowing through the first inlet header 3 turns into a two-phase gas-liquid state, similar advantages can be achieved by making the high-temperature fluid flow into the through-holes in the first flat pipes 1 from the first inlet header 3 in a substantially horizontal direction.
  • the configuration of the heat exchanger 10 according to Example 1 is merely an example; for example, the heat exchanger 10 may be configured as follows. The following description will mainly be focused on the differences from the heat exchanger 10 according to Example 1.
  • FIG. 6 includes side views illustrating examples of a heat exchanger according to Example 2 which lies outside the scope of the claimed invention.
  • the bent segments 2b of each second flat pipe 2 are substantially U-shaped in cross section.
  • the bent segment 2b that connects the inflow segment 2a and the heat exchanging segment 2c of the second flat pipe 2 is disposed so as to overpass the first outlet header 4 through which the high-temperature fluid flows.
  • the bent segment 2b that connects the heat exchanging segment 2c and the outflow segment 2d of the second flat pipe 2 is disposed so as to overpass the first inlet header 3 through which the high-temperature fluid flows.
  • the heat exchanger 10 having such a configuration achieves compactness since the height of the flat pipes 1 and 2 is reduced in the stacked direction thereof.
  • each first flat pipe 1 has an inflow segment 1a, a heat exchanging segment 1c, an outflow segment 1d, and bent segments 1b.
  • the inflow segment 1a is connected to the first inlet header 3 and has a substantially horizontal passage.
  • the outflow segment 1d is connected to the first outlet header 4 and has a substantially horizontal passage.
  • the heat exchanging segment 1c and the heat exchanging segment 2c of the second flat pipe 2 are stacked such that flat surfaces thereof are in contact with each other.
  • the bent segments 1b connect between the inflow segment 1a and the heat exchanging segment 1c, as well as between the heat exchanging segment 1c and the outflow segment 1d.
  • each first flat pipe 1 at the first inlet header 3 side is bent in the same direction as the end of each second flat pipe 2 at the second outlet header 6 side.
  • the end of each first flat pipe 1 at the first outlet header 4 side is bent in the same direction as the end of each second flat pipe 2 at the second inlet header 5 side.
  • the heat exchanger 10 having such a configuration is advantageous in that the installation space can be made compact in the height direction when a plurality of heat exchangers 10 are installed.
  • the installation space can be made compact in the height direction when a plurality of heat exchangers 10 are installed.
  • gaps between the heat exchangers 10 in the height direction can be reduced while interference between the headers 3, 4, 5, and 6 is prevented.
  • Second flat pipes 2A disposed above the first flat pipes 1 each have an inflow segment 2Aa, a heat exchanging segment 2Ac, an outflow segment 2Ad, and bent segments 2Ab.
  • the inflow segment 2Aa is connected to a second inlet header 5A and has a substantially horizontal passage.
  • the outflow segment 2Ad is connected to a second outlet header 6A and has a substantially horizontal passage.
  • the heat exchanging segment 2Ac and the corresponding first flat pipe 1 are stacked such that flat surfaces thereof are in contact with each other.
  • the bent segments 2Ab connect between the inflow segment 2Aa and the heat exchanging segment 2Ac, as well as between the heat exchanging segment 2Ac and the outflow segment 2Ad.
  • the ends of each second flat pipe 2A are bent so as to extend upon the first inlet header 3 and the first outlet header 4.
  • Second flat pipes 2B disposed below the first flat pipes 1 each have an inflow segment 2Ba, a heat exchanging segment 2Bc, an outflow segment 2Bd, and bent segments 2Bb.
  • the inflow segment 2Ba is connected to a second inlet header 5B and has a substantially horizontal passage.
  • the outflow segment 2Bd is connected to a second outlet header 6B and has a substantially horizontal passage.
  • the heat exchanging segment 2Bc and the corresponding first flat pipe 1 are stacked such that flat surfaces thereof are in contact with each other.
  • the bent segments 2Bb connect between the inflow segment 2Ba and the heat exchanging segment 2Bc, as well as between the heat exchanging segment 2Bc and the outflow segment 2Bd.
  • the ends of each second flat pipe 2B are bent so as to extend under the first inlet header 3 and the first outlet header 4.
  • the low-temperature fluid in the two-phase gas-liquid state is made to flow out toward the through-holes 21 in the second flat pipes 2B in a substantially horizontal direction. Therefore, similar to Example 1, the gas-to-liquid ratio of the low-temperature fluid distributed to the through-holes 21 can be made uniform, whereby a compact, high-performance heat exchanger 10 can be obtained.
  • the heat exchanger 10 according to each of Example 1 and Example 2 is installed in, for example, a refrigeration and air-conditioning apparatus, such as an air-conditioning apparatus, a hot-water storage apparatus, or a refrigeration apparatus.
  • a refrigeration and air-conditioning apparatus such as an air-conditioning apparatus, a hot-water storage apparatus, or a refrigeration apparatus.
  • An example of a refrigeration and air-conditioning apparatus equipped with the heat exchanger 10 according to Example 1 or Example 2 will be described below.
  • FIG. 7 is a refrigerant circuit diagram illustrating an example of a refrigeration and air-conditioning apparatus according to Example 3 which equally lies outside the scope of the claimed invention.
  • the refrigeration and air-conditioning apparatus shown in FIG. 7 has a first refrigerant circuit in which a first compressor 30, a first radiator 31, a first pressure reducing device 32, and a first cooling unit 33 are connected in that order with pipes.
  • the first refrigerant circuit makes a first refrigerant serving as a high-temperature fluid circulate therethrough and operates based on a vapor compression refrigeration cycle.
  • the heat exchanger 10 is disposed between the first radiator 31 and the first pressure reducing device 32 in the first refrigerant circuit.
  • the first inlet header 3 of the heat exchanger 10 is connected to the first radiator 31, and the first outlet header 4 is connected to the first pressure reducing device 32.
  • the refrigeration and air-conditioning apparatus also has a second refrigerant circuit in which the heat exchanger 10, a second compressor 40, a second radiator 41, and a second pressure reducing device 42 are connected in that order with pipes.
  • the second outlet header 6 of the heat exchanger 10 is connected to the second compressor 40, and the second inlet header 5 is connected to the second pressure reducing device 42.
  • the second refrigerant circuit makes a second refrigerant serving as a low-temperature fluid circulate therethrough and operates based on a vapor compression refrigeration cycle.
  • the first refrigerant and the second refrigerant used are a refrigerant such as carbon dioxide, an HFC-based refrigerant, an HC-based refrigerant, an HFO-based refrigerant, and ammonia.
  • carbon dioxide is used as the first refrigerant.
  • the first refrigerant is compressed by the first compressor 30 and is discharged therefrom as a high-temperature high-pressure supercritical fluid.
  • the first refrigerant having become a high-temperature high-pressure supercritical fluid is transported to the first radiator 31 and is decreased in temperature by exchanging heat with air or the like at the first radiator 31, thereby becoming a high-pressure supercritical fluid.
  • the first refrigerant having become a high-pressure supercritical fluid is decreased in temperature by being cooled by the heat exchanger 10, flows into the first pressure reducing device 32 where the first refrigerant is decompressed so as to change into a low-temperature low-pressure two-phase gas-liquid state, and is then transported to the first cooling unit 33.
  • the first refrigerant in the low-temperature low-pressure two-phase gas-liquid state evaporates by exchanging heat with air or the like at the first cooling unit 33 and then returns to the first compressor 30.
  • the second refrigerant is compressed by the second compressor 40 and is discharged therefrom as high-temperature high-pressure vapor.
  • the second refrigerant having becoming high-temperature high-pressure vapor is transported to the second radiator 41 and is decreased in temperature by exchanging heat with air or the like at the second radiator 41, thereby becoming a high-pressure liquid.
  • the second refrigerant having become a high-pressure liquid is decompressed by the second pressure reducing device 42 so as to change into a low-temperature two-phase gas-liquid state, and is transported to the heat exchanger 10.
  • the second refrigerant in the low-temperature two-phase gas-liquid state becomes vapor by being heated at the heat exchanger 10 and then returns to the second compressor 40.
  • the efficiency of the refrigeration and air-conditioning apparatus is improved by ensuring a large degree of subcooling for the refrigerant flowing out from the first radiator 31.
  • the efficiency of the refrigeration and air-conditioning apparatus is improved especially when the first refrigerant in the first refrigerant circuit is carbon dioxide and transfers heat at a critical point or higher.
  • the second refrigerant circuit is described as being a vapor compression refrigeration cycle in Example 3, the second refrigerant may alternatively be water or brine (antifreeze), such as an ethylene glycol aqueous solution, and the second compressor 40 may alternatively be a pump.
  • water or brine antifreeze
  • the second compressor 40 may alternatively be a pump.
  • FIG. 8 is a refrigerant circuit diagram illustrating another example of the refrigeration and air-conditioning apparatus according to Example 3.
  • the first radiator 31 is omitted from the configuration of the refrigeration and air-conditioning apparatus shown in FIG. 7 , and the first refrigerant, which is high-temperature high-pressure vapor, discharged from the first compressor 30 is entirely cooled at the heat exchanger 10.
  • the refrigeration and air-conditioning apparatus shown in FIG. 8 is a so-called secondary-loop refrigeration and air-conditioning apparatus.
  • the heat exchanger 10 is used as the first radiator 31.
  • the amount of heat exchange required in the heat exchanger 10 is increased, and the percentage of volume occupying the overall refrigeration and air-conditioning apparatus becomes larger than in the case where the first radiator 31 is provided.
  • the heat exchanger 10 made compact the advantage in which the entire refrigeration and air-conditioning apparatus is made compact is further increased.
  • FIG. 9 is a refrigerant circuit diagram illustrating another example of the refrigeration and air-conditioning apparatus according to Example 3.
  • the refrigeration and air-conditioning apparatus shown in FIG. 9 has a refrigerant circuit in which the first compressor 30, the first radiator 31, the first pressure reducing device 32, and the first cooling unit 33 are connected in that order. Furthermore, the refrigeration and air-conditioning apparatus shown in FIG. 9 has a bypass pipe 52.
  • the bypass pipe 52 has one end connected between the first radiator 31 and the first pressure reducing device 32 and other end connected to an injection port 53, which is provided at an intermediate position in a refrigerant compression process in the first compressor 30, or between the compressor 30 and the first cooling unit 33, although not shown here.
  • the heat exchanger 10 is disposed between the first radiator 31 and the first pressure reducing device 32 in the refrigerant circuit and at an intermediate position of the bypass pipe 52.
  • the first inlet header 3 is connected to the first radiator 31, and the first outlet header 4 is connected to the first pressure reducing device 32.
  • the second inlet header 5 is connected to a bypass pressure reducing device 51, and the second outlet header 6 is connected to the injection port 53 or between the compressor 30 and the first cooling unit 33, although not shown here.
  • a refrigerant (i.e., low-temperature fluid) decompressed by the bypass pressure reducing device 51 changes into a low-temperature two-phase gas-liquid state, exchanges heat at the heat exchanger 10 with a refrigerant (i.e., high-temperature fluid) flowing out from the first radiator 31, and is then transported to the injection port 53 of the first compressor 30.
  • a refrigerant such as an HFC-based refrigerant, an HC-based refrigerant, an HFO-based refrigerant, ammonia, and carbon dioxide is used in the refrigeration and air-conditioning apparatus shown in FIG. 9 .
  • the flow rate of refrigerant flowing through the first cooling unit 33 can be reduced without reducing the refrigeration effect, as compared with a case where the heat exchanger 10 is not used. This is effective especially if the pipe length between the first compressor 30 and the first cooling unit 33 is large since deterioration in performance caused by an increase in pressure loss can be suppressed.
  • the first flat pipes 1 through which the high-temperature fluid flows and the second flat pipes 2 through which the low-temperature fluid flows are formed independently of each other, and the first flat pipes 1 and the second flat pipes 2 are stacked such that the flat surfaces thereof are joined together by soldering or the like.
  • the refrigerant passages through which the high-temperature fluid flows and the refrigerant passages through which the low-temperature fluid flows are formed in separate components.
  • the refrigerant passages through which the high-temperature fluid flows and the refrigerant passages through which the low-temperature fluid flows may be formed in the same component (in other words, the first passage section and the second passage section according to the present invention may be integrally formed).
  • the heat exchanger 10 having such a configuration may be installed in the refrigeration and air-conditioning apparatus according to Example 3.
  • items not described in particular are the same as those in Example 1 to Example 3.
  • FIG. 10 includes structural diagrams of a heat exchanger according to Embodiment 1 of the present invention. Specifically, FIG. 10(a) is a perspective view of the heat exchanger 10, and FIG. 10(b) is a diagram as viewed along an arrow A in FIG. 10(a) .
  • a plurality of first refrigerant passages 101a through which a first refrigerant (e.g., a high-temperature fluid) flows extend through a main body 110 of the heat exchanger 10 according to Embodiment 1 in, for example, the longitudinal direction (i.e., the up-down direction in FIG. 10 ).
  • a first refrigerant path 101 is formed.
  • second refrigerant passages 102a through which a second refrigerant (e.g., a low-temperature fluid) flows extend through the main body 110 in, for example, the longitudinal direction (i.e., the up-down direction in FIG. 10 ).
  • a second refrigerant path 102 is formed.
  • the first refrigerant path 101 and the second refrigerant 102 are disposed such that the parallel-arranged direction of the first refrigerant passages 101a and the parallel-arranged direction of the second refrigerant passages 102a are aligned with each other.
  • the first refrigerant path 101 i.e., the first refrigerant passages 101a
  • the second refrigerant path 102 i.e., the second refrigerant passages 102a
  • the first refrigerant path 101 and the second refrigerant path 102 are integrally formed.
  • the main body 110 having the first refrigerant path 101 and the second refrigerant path 102 is composed of, for example, aluminum or an aluminum alloy, copper or a copper alloy, steel, or a stainless alloy, and is manufactured by extrusion, pultrusion or the like.
  • One of two ends of the main body 110 in the refrigerant flowing direction is provided with a second inlet communication hole 105a that extends in the parallel-arranged direction of the second refrigerant passages 102a and communicates with all of the second refrigerant passages 102a.
  • the other end is provided with a second outlet communication hole 106a that extends in the parallel-arranged direction of the second refrigerant passages 102a and communicates with all of the second refrigerant passages 102a.
  • the second inlet communication hole 105a and the second outlet communication hole 106a are horizontally disposed.
  • the one end that is provided with the second outlet communication hole 106a is provided with a first inlet communication hole 103a that extends in the parallel-arranged direction of the first refrigerant passages 101a and communicates with all of the first refrigerant passages 101a.
  • the other end that is provided with the second inlet communication hole 105a is provided with a first outlet communication hole 104a that extends in the parallel-arranged direction of the first refrigerant passages 101a and communicates with all of the first refrigerant passages 101a.
  • the first inlet communication hole 103a and the first outlet communication hole 104a are horizontally disposed.
  • first inlet communication hole 103a and the second outlet communication hole 106a are slightly displaced relative to each other in the refrigerant flowing direction of the first refrigerant passages 101a (in other words, the second refrigerant passages 102a).
  • first outlet communication hole 104a and the second inlet communication hole 105a are slightly displaced relative to each other in the refrigerant flowing direction of the first refrigerant passages 101a (in other words, the second refrigerant passages 102a).
  • the extending direction of the first inlet communication hole 103a and the first outlet communication hole 104a do not necessarily need to be orthogonal to the direction of the first refrigerant passages 101a. Furthermore, the extending direction of the second inlet communication hole 105a and the second outlet communication hole 106a do not necessarily need to be orthogonal to the direction of the second refrigerant passages 102a.
  • the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, and the second outlet communication hole 106a each have one open end and are respectively connected to a first inlet connection pipe 103, a first outlet connection pipe 104, a second inlet connection pipe 105, and a second outlet connection pipe 106 so as to communicate with the outside.
  • the other end of each of the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, and the second outlet communication hole 106a is closed by a sealing member or the like.
  • the open (or closed) ends of the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, and the second outlet communication hole 106a are all located at the same side.
  • the open (or closed) ends of the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, and the second outlet communication hole 106a are not limited to the positions shown in FIG. 10 and do not need to be located at the same side so long as each communication hole has an open end and a closed end.
  • Both ends of each of the plurality of first refrigerant passages 101a and second refrigerant passages 102a extending through the main body 110 in the longitudinal direction are sealed by a process such as pinching or sealed by using sealing members (not shown).
  • the heat exchanger 10 according to Embodiment 1 is assumed to be used in a position that makes the low-temperature fluid and the high-temperature fluid flow in the up-down direction as shown in FIG. 10 . Furthermore, in the heat exchanger 10 according to Embodiment 1, the low-temperature fluid in a two-phase gas-liquid state is assumed to flow into the second refrigerant passages 102a of the second refrigerant path via the second inlet connection pipe 105 and the second inlet communication hole 105a.
  • the second inlet communication hole 105a is disposed at the following position based on the information obtained from the tests shown in FIGs. 3 to 5 in Example 1, that is, the ranges of the aforementioned position angles ⁇ , ⁇ , and ⁇ providing excellent heat transfer characteristics.
  • the central axis of the second inlet communication hole 105a is arranged off a center line of the second refrigerant path 102 (i.e. the second refrigerant passages 102a) in a direction away from the first refrigerant path 101 (i.e. the first refrigerant passages 101a).
  • the second refrigerant path 102 and the second inlet header 5 are connected with a position angle ⁇ that may be in a range of 0° ⁇ ⁇ ⁇ 110° (or -110° ⁇ ⁇ ⁇ 0 if the positive direction is the same as in FIG. 3 ).
  • the first refrigerant path 101, the second refrigerant path 102, the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, and the second outlet communication hole 106a respectively correspond to the "first passage section", the "second passage section”, the "first inlet header”, the “first outlet header”, the “second inlet header”, and the “second outlet header” according to the present invention.
  • the high-temperature fluid flows into the first inlet communication hole 103a via the first inlet connection pipe 103, flows through the first refrigerant path 101 and the first outlet communication hole 104a in that order, and then flows out from the first outlet connection pipe 104.
  • the low-temperature fluid in a two-phase gas-liquid state flows into the second inlet communication hole 105a via the second inlet connection pipe 105, flows through the second refrigerant path 102 and the second outlet communication hole 106a in that order, and then flows out from the second outlet connection pipe 106.
  • the high-temperature fluid flowing through the first refrigerant path 101 and the low-temperature fluid flowing through the second refrigerant path 102 exchange heat in a countercurrent manner via a partition wall between the refrigerant paths.
  • the central axis of the second inlet communication hole 105a is arranged off a center line of the second refrigerant path 102 (i.e. the second refrigerant passages 102a) in a direction away from the first refrigerant path 101 (i.e. the first refrigerant passages 101a).
  • the position angle ⁇ when the low-temperature fluid in the two-phase gas-liquid state flows into the second refrigerant path 102 from the second inlet communication hole 105a is in a range of 0° ⁇ ⁇ ⁇ 110°. Therefore, the low-temperature fluid in the two-phase gas-liquid state is readily distributed to the second refrigerant passages 102a of the second refrigerant path 102 with a substantially uniform gas-to-liquid ratio, whereby a heat exchanger 10 with stable performance can be obtained.
  • Example 1 It is apparent from Example 1 that, if the direction indicated by an arrow in FIG. 10(b) is defined as the positive direction, the distribution characteristics of a gaseous phase component and a liquid phase component in the low-temperature fluid are optimal when 80° ⁇ ⁇ ⁇ 100°. Moreover, the distance between the first refrigerant path 101 and the second refrigerant path 102 located next to each other can be shortened.
  • the second inlet communication hole 105a is formed so as to satisfy 80° ⁇ ⁇ ⁇ 100°, thereby further suppressing heat resistance in the main body 110 due to heat conductivity and further improving the performance of the heat exchanger 10.
  • first refrigerant path 101 and the second refrigerant path 102 formed integrally in the main body 110, the following various advantages can also be achieved.
  • first inlet communication hole 103a and the first outlet communication hole 104a are provided inside the main body 110 of the heat exchanger 10, an additional header pipe for connecting to the first refrigerant path 101 is not necessary, thereby achieving compactness of the heat exchanger 10, as well as simplifying the manufacturing process.
  • second inlet communication hole 105a and the second outlet communication hole 106a with respect to the second refrigerant path 102.
  • the distance between the first refrigerant path 101 and the second refrigerant path 102 located next to each other can be shortened, as compared with a case where the holes are not displaced, thereby achieving compactness of the heat exchanger 10.
  • first refrigerant passages 101a and the second refrigerant passages 102a are rectangular in cross section, as shown in FIG. 10
  • the cross-sectional shapes thereof are not limited to a rectangular shape.
  • the cross-sectional shape of the first refrigerant passages and the second refrigerant passages 102a may be polygonal, or circular for enhancing the pressure resisting performance, for example.
  • the first refrigerant passages and the second refrigerant passages 102a may certainly be elongated or ellipsoidal in cross section. In this case, it is needless to say that the cross-sectional shape of the first refrigerant passages 101a and the cross-sectional shape of the second refrigerant passages 102a do not need to be the same.
  • the heat transfer area may be increased by providing a groove in the inner surface of each of the first refrigerant passages and the second refrigerant passages 102a.
  • these grooves may be processed simultaneously during the extrusion process or the pultrusion process of the main body 10 so that the manufacturing process can be simplified.
  • first refrigerant passages in the first refrigerant path 101 and the number of second refrigerant passages 102a in the second refrigerant path 102 are the same in the heat exchanger 10 according to Embodiment 1, as shown in FIG. 10 , the numbers thereof are not limited to this relationship. Specifically, the numbers may be varied in accordance with the operating conditions or the flow property values of the high-temperature fluid and the low-temperature fluid in the heat exchanger 10 so that a preferred heat exchanger 10 with high heat transfer performance and low pressure loss is achieved.
  • the two fluids may alternatively exchange heat in a parallel current manner.
  • the high-temperature fluid flowing through the first refrigerant path 101 and the low-temperature fluid flowing through the second refrigerant path 102 exchange heat in a countercurrent manner
  • the two fluids may alternatively exchange heat in a parallel current manner.
  • the high-temperature fluid and the low-temperature fluid are made to flow in parallel to each other.
  • the heat exchanger 10 in FIG. 10 is described as being used in a position that makes the low-temperature fluid and the high-temperature fluid flow in the up-down direction
  • the installation position of the heat exchanger 10 according to Embodiment 1 in which the first refrigerant path 101 and the second refrigerant path 102 are integrally formed is not limited to the position shown in FIG. 10 .
  • FIG. 11 includes structural diagrams illustrating another example of the heat exchanger according to Embodiment 1 of the present invention. Specifically, FIG. 11(a) is a perspective view of the heat exchanger 10, and FIG. 11(b) is a diagram as viewed along an arrow A in FIG. 11(a) .
  • the heat exchanger 10 shown in FIG. 11 is assumed to be used in a position that makes the low-temperature fluid and the high-temperature fluid flow in the left-right direction (i.e., substantially horizontal direction).
  • the first refrigerant path 101 i.e., the first refrigerant passages 101a
  • the second refrigerant path 102 i.e., the second refrigerant passages 102a
  • the remaining configuration is similar to that in the heat exchanger 10 shown in FIG. 10 and exhibits similar advantages. Since components given the same reference numerals in FIGs. 10 and 11 have the same functions and operate in the same manner, descriptions of the functions and operations thereof will be omitted.
  • the central axis of the second inlet communication hole 105a may similarly be disposed at a position that is aligned with the connection section between the second inlet communication hole 105a and the second refrigerant path 102 (i.e., the second refrigerant passages 102a), or at a position away from the first refrigerant path 101 (i.e., the first refrigerant passages 101a) relative to the connection section.
  • the position angle ⁇ when the low-temperature fluid in the two-phase gas-liquid state flows into the second refrigerant path 102 from the second inlet communication hole 105a can be set in a range of 0° ⁇ ⁇ ⁇ 90°. Therefore, the low-temperature fluid in the two-phase gas-liquid state is readily distributed to the second refrigerant passages 102a of the second refrigerant path 102 with a substantially uniform gas-to-liquid ratio, whereby a heat exchanger 10 with stable performance can be obtained.
  • a range of 80° ⁇ ⁇ ⁇ 100° is the most preferable as the distribution characteristics
  • the distance between the first refrigerant path 101 and the second refrigerant path 102 located next to each other can be shorter. Therefore, a position angle ⁇ that allows for reduced heat resistance by heat conductivity and improved performance may at least be in the range of 0° ⁇ ⁇ ⁇ 90°.
  • a usage mode in which the low-temperature fluid in the two-phase gas-liquid state is made to flow in from the second outlet connection pipe 106 and flow out from the second inlet connection pipe 105 may also be assumed.
  • the central axis of the second outlet communication hole 106a is disposed at a position aligned with a connection section between the second outlet communication hole 106a and the second refrigerant path 102 (i.e., the second refrigerant passages 102a), or at a position away from the first refrigerant path 101 (i.e., the first refrigerant passages 101a) relative to the connection section.

Landscapes

  • 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)

Claims (2)

  1. Échangeur de chaleur (10) comprenant:
    - une première section de passage (101), agencée verticalement ou horizontalement, dans laquelle une pluralité de trous traversants (101a) à travers lesquels un fluide à haute température peut s'écouler sont agencés parallèlement les uns aux autres;
    - une deuxième section de passage (102), agencée verticalement ou horizontalement, dans laquelle une pluralité de trous traversants (102a) à travers lesquels un fluide à basse température peut s'écouler sont agencés parallèlement les uns aux autres;
    - un premier collecteur d'entrée (103a) agencé horizontalement, ayant une forme tubulaire et connecté à une extrémité de la première section de passage (101);
    - un premier collecteur de sortie (104a) agencé horizontalement, ayant une forme tubulaire et connecté à l'autre extrémité de la première section de passage (101);
    - un deuxième collecteur d'entrée (105a) agencé horizontalement, ayant une forme tubulaire et connecté à une extrémité de la deuxième section de passage (102);
    - un deuxième collecteur de sortie (106a) agencé horizontalement, ayant une forme tubulaire et connecté à l'autre extrémité de la deuxième section de passage (102); dans lequel la première section de passage (101), la deuxième section de passage (102), le premier collecteur d'entrée (103a), le premier collecteur de sortie (104a), le deuxième collecteur d'entrée (105a) et le deuxième collecteur de sortie (106a) sont formés intégralement,
    dans lequel la première section de passage (101) et la deuxième section de passage (102) sont agencées avec des directions agencées en alignement parallèle de leurs trous traversants (101a, 102a) de manière à être capables d'échanger de la chaleur par l'intermédiaire d'une paroi de cloisonnement prévue entre les deux,
    dans lequel le fluide à basse température qui peut s'écouler jusque dans les trous traversants (102a) dans la deuxième section de passage (102) depuis le deuxième collecteur d'entrée (105a) peut être un fluide dans un état à deux phases gaz/liquide, caractérisé en ce que,
    dans un état où le deuxième collecteur d'entrée (105a) est observé dans une direction d'axe central du deuxième collecteur d'entrée (105a), un axe central du deuxième collecteur d'entrée (105a) est agencé à l'extérieur d'une ligne centrale de la deuxième section de passage (102) dans une direction en éloignement de la première section de passage (101).
  2. Appareil de réfrigération et de conditionnement d'air équipé de l'échangeur de chaleur selon la revendication 1.
EP11814315.5A 2010-08-05 2011-08-05 Échangeur de chaleur et dispositif de conditionnement d'air et de réfrigération Active EP2602578B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010176044 2010-08-05
PCT/JP2011/004459 WO2012017681A1 (fr) 2010-08-05 2011-08-05 Échangeur de chaleur et dispositif de conditionnement d'air et de réfrigération

Publications (3)

Publication Number Publication Date
EP2602578A1 EP2602578A1 (fr) 2013-06-12
EP2602578A4 EP2602578A4 (fr) 2015-03-11
EP2602578B1 true EP2602578B1 (fr) 2019-01-23

Family

ID=45559200

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11814315.5A Active EP2602578B1 (fr) 2010-08-05 2011-08-05 Échangeur de chaleur et dispositif de conditionnement d'air et de réfrigération

Country Status (5)

Country Link
US (1) US20130126127A1 (fr)
EP (1) EP2602578B1 (fr)
JP (1) JP5777622B2 (fr)
CN (1) CN103069245A (fr)
WO (1) WO2012017681A1 (fr)

Families Citing this family (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5784215B2 (ja) * 2012-03-07 2015-09-24 三菱電機株式会社 熱交換器および冷凍サイクル装置
JP5759068B2 (ja) * 2012-05-17 2015-08-05 三菱電機株式会社 熱交換器及び冷凍サイクル装置
JP5790730B2 (ja) 2012-12-25 2015-10-07 ダイキン工業株式会社 熱交換器
WO2015004720A1 (fr) * 2013-07-08 2015-01-15 三菱電機株式会社 Échangeur de chaleur, et appareil de conditionnement de l'air
JP6315945B2 (ja) * 2013-11-08 2018-04-25 三菱電機株式会社 熱交換器
EP3077755B1 (fr) * 2013-12-04 2020-02-05 Zehnder Group International AG Batteries de tubes pour un radiateur de chauffage et radiateur de chauffage muni de batteries de tubes de ce type
CN209054801U (zh) * 2016-03-31 2019-07-02 三菱电机株式会社 热交换器以及制冷循环装置
JP2017215130A (ja) * 2016-06-02 2017-12-07 サンデンホールディングス株式会社 車両用内部熱交換器
CN107796143A (zh) * 2017-07-13 2018-03-13 杭州三花研究院有限公司 换热器及制冷系统
JP6493575B1 (ja) * 2018-01-31 2019-04-03 ダイキン工業株式会社 冷凍装置
JP7202851B2 (ja) * 2018-11-05 2023-01-12 三菱重工業株式会社 熱交換器及びそれを備えたボイラ、並びに熱交換方法
JPWO2020100897A1 (ja) * 2018-11-12 2021-06-10 三菱電機株式会社 熱交換器及び熱交換器の製造方法
CN111322795A (zh) * 2018-12-14 2020-06-23 丹佛斯有限公司 换热器和空调系统
CN110230902B (zh) * 2019-02-01 2024-07-12 广东美的暖通设备有限公司 微通道扁管、换热器和热泵系统
EP3936791A4 (fr) * 2019-03-05 2022-03-09 Mitsubishi Electric Corporation Échangeur de chaleur et dispositif à cycle de réfrigération
JP7037076B2 (ja) * 2019-05-10 2022-03-16 ダイキン工業株式会社 熱交換器、ヒートポンプ装置および熱交換器の製造方法
US20210278147A1 (en) * 2020-03-05 2021-09-09 Uchicago Argonne, Llc Additively Manufactured Modular Heat Exchanger Accommodating High Pressure, High Temperature and Corrosive Fluids
BR112023000336A2 (pt) * 2020-08-26 2023-03-14 Midea Group Co Ltd Trocador de calor, caixa de controle elétrico e sistema de ar-condicionado.
CN214676259U (zh) * 2020-08-26 2021-11-09 广东美的暖通设备有限公司 空调装置以及电控盒
CN114111390B (zh) * 2020-08-26 2023-11-10 广东美的暖通设备有限公司 换热器、电控盒以及空调系统
US20230184445A1 (en) * 2020-08-26 2023-06-15 Gd Midea Heating & Ventilating Equipment Co., Ltd. Air conditioning apparatus and electric control box
WO2022042559A1 (fr) 2020-08-26 2022-03-03 广东美的暖通设备有限公司 Dispositif de climatisation et boîtier de commande électrique
CN114909715B (zh) * 2021-02-08 2024-03-22 广东美的暖通设备有限公司 换热器及其制造方法、电控盒以及空调系统
CN114909831B (zh) * 2021-02-08 2024-06-14 广东美的暖通设备有限公司 换热器、电控盒及空调系统
CN115235149B (zh) * 2022-06-22 2023-10-31 西安交通大学 一种用于低温冰箱或冷柜的盘式微通道回热器及工作方法

Family Cites Families (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3979923A (en) * 1975-08-04 1976-09-14 Jennings John H Preassembled refrigerant subcooling unit
JPH0239122Y2 (fr) * 1985-05-02 1990-10-22
JPH0258665U (fr) * 1988-10-18 1990-04-26
US5309637A (en) * 1992-10-13 1994-05-10 Rockwell International Corporation Method of manufacturing a micro-passage plate fin heat exchanger
JP3092484B2 (ja) * 1994-07-22 2000-09-25 三菱電機株式会社 熱交換器及びその製造方法、冷凍システム、空調装置、熱交換器の製造装置及びその治具
JPH0968371A (ja) * 1995-08-31 1997-03-11 Nippon Soken Inc 気液分離器
US6032726A (en) * 1997-06-30 2000-03-07 Solid State Cooling Systems Low-cost liquid heat transfer plate and method of manufacturing therefor
US6354002B1 (en) * 1997-06-30 2002-03-12 Solid State Cooling Systems Method of making a thick, low cost liquid heat transfer plate with vertically aligned fluid channels
JP2000249479A (ja) * 1999-02-26 2000-09-14 Matsushita Electric Ind Co Ltd 熱交換器
US6347528B1 (en) * 1999-07-26 2002-02-19 Denso Corporation Refrigeration-cycle device
JP2002340485A (ja) * 2001-05-15 2002-11-27 Mitsubishi Heavy Ind Ltd 車両用熱交換器
JP3945208B2 (ja) * 2001-10-09 2007-07-18 株式会社デンソー 熱交換用チューブ及び熱交換器
JP3826791B2 (ja) * 2002-01-07 2006-09-27 株式会社デンソー 熱交換器
JP2003279276A (ja) * 2002-03-19 2003-10-02 Toyo Radiator Co Ltd 熱交換器
US20030178188A1 (en) * 2002-03-22 2003-09-25 Coleman John W. Micro-channel heat exchanger
JP4179092B2 (ja) * 2003-07-30 2008-11-12 株式会社デンソー 熱交換器
JP2005127611A (ja) * 2003-10-23 2005-05-19 Mitsubishi Heavy Ind Ltd 熱交換器
US7124805B2 (en) * 2004-05-24 2006-10-24 Modine Manufacturing Company Tube feature for limiting insertion depth into header slot
JP4561305B2 (ja) * 2004-10-18 2010-10-13 三菱電機株式会社 熱交換器
JP4742233B2 (ja) * 2005-05-13 2011-08-10 株式会社東芝 セラミックス製熱交換器
JP4521513B2 (ja) * 2006-01-30 2010-08-11 独立行政法人産業技術総合研究所 内部発熱式の熱交換構造体
JP2007278624A (ja) * 2006-04-07 2007-10-25 Denso Corp ヒートポンプサイクル
ES2447776T3 (es) * 2006-04-14 2014-03-12 Mitsubishi Denki Kabushiki Kaisha Intercambiador de calor y acondicionador de aire refrigerante
JP4867569B2 (ja) * 2006-10-19 2012-02-01 三菱電機株式会社 熱交換器および冷凍空調装置
DE102006055837A1 (de) * 2006-11-10 2008-05-15 Visteon Global Technologies Inc., Van Buren Wärmeübertrager, insbesondere als Verdampfer von Fahrzeugklimaanlagen
JP2009121758A (ja) * 2007-11-15 2009-06-04 Mitsubishi Electric Corp 熱交換器および冷熱システム
CN201392114Y (zh) * 2009-04-16 2010-01-27 大冶斯瑞尔换热器有限公司 高、低温水高效换热器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
JPWO2012017681A1 (ja) 2013-10-03
EP2602578A4 (fr) 2015-03-11
WO2012017681A1 (fr) 2012-02-09
CN103069245A (zh) 2013-04-24
JP5777622B2 (ja) 2015-09-09
EP2602578A1 (fr) 2013-06-12
US20130126127A1 (en) 2013-05-23

Similar Documents

Publication Publication Date Title
EP2602578B1 (fr) Échangeur de chaleur et dispositif de conditionnement d'air et de réfrigération
JP5071597B2 (ja) 熱交換器および空気調和機
WO2007013439A1 (fr) Échangeur de chaleur
JP2012163328A5 (fr)
JP2002206890A (ja) 熱交換器およびこれを用いた冷凍空調サイクル装置
WO2018047332A1 (fr) Collecteur, échangeur de chaleur et climatiseur
WO2017150126A1 (fr) Échangeur de chaleur et climatiseur
US20140144611A1 (en) Heat exchanger and refrigeration cycle apparatus equipped with the same
KR20120044851A (ko) 열교환기
JP6373456B2 (ja) ヘッダーおよび空気調和装置
EP2982924A1 (fr) Échangeur de chaleur
CN110595111B (zh) 换热器和多制冷系统空调机组
WO2018154650A1 (fr) Échangeur de chaleur
JPWO2019003428A1 (ja) 熱交換器、及び冷凍サイクル装置
KR20040075717A (ko) 열교환기
KR101149725B1 (ko) 열교환기
JP2014137172A (ja) 熱交換器及び冷凍装置
WO2012153490A1 (fr) Échangeur de chaleur et dispositif à cycle froid équipé de celui-ci
JP4867569B2 (ja) 熱交換器および冷凍空調装置
JP6315945B2 (ja) 熱交換器
JP2005016866A (ja) 熱交換器
JP2005024188A (ja) 熱交換器
US20230033824A1 (en) Air conditioning system, and heat exchange system for heat dissipation of electronic control assembly of air conditioning system
CN216347958U (zh) 换热器及电器设备
WO2022215164A1 (fr) Échangeur de chaleur et climatiseur

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20130201

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20150205

RIC1 Information provided on ipc code assigned before grant

Ipc: F28D 7/00 20060101ALI20150130BHEP

Ipc: F28D 7/16 20060101AFI20150130BHEP

Ipc: F28F 1/02 20060101ALN20150130BHEP

Ipc: F28D 1/02 20060101ALN20150130BHEP

Ipc: F25B 39/04 20060101ALI20150130BHEP

Ipc: F28F 7/02 20060101ALI20150130BHEP

Ipc: F25B 39/00 20060101ALN20150130BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20180118

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

RIC1 Information provided on ipc code assigned before grant

Ipc: F28F 7/02 20060101ALI20180704BHEP

Ipc: F28F 1/02 20060101ALN20180704BHEP

Ipc: F25B 39/04 20060101ALI20180704BHEP

Ipc: F28D 1/02 20060101ALN20180704BHEP

Ipc: F28D 7/00 20060101ALI20180704BHEP

Ipc: F25B 39/00 20060101ALN20180704BHEP

Ipc: F28D 7/16 20060101AFI20180704BHEP

INTG Intention to grant announced

Effective date: 20180806

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1091778

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190215

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602011055966

Country of ref document: DE

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190123

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190523

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190423

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1091778

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190123

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190424

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190523

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190423

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602011055966

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

26N No opposition filed

Effective date: 20191024

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190805

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190831

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190831

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20190831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190805

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20110805

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

REG Reference to a national code

Ref country code: DE

Ref legal event code: R084

Ref document number: 602011055966

Country of ref document: DE

REG Reference to a national code

Ref country code: GB

Ref legal event code: 746

Effective date: 20220510

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190123

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230512

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20230629

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20230630

Year of fee payment: 13

Ref country code: FR

Payment date: 20230703

Year of fee payment: 13

Ref country code: DE

Payment date: 20230627

Year of fee payment: 13