EP3910262B1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

Info

Publication number
EP3910262B1
EP3910262B1 EP19908451.8A EP19908451A EP3910262B1 EP 3910262 B1 EP3910262 B1 EP 3910262B1 EP 19908451 A EP19908451 A EP 19908451A EP 3910262 B1 EP3910262 B1 EP 3910262B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
internal heat
refrigeration cycle
evaporator
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
EP19908451.8A
Other languages
German (de)
English (en)
Other versions
EP3910262A1 (fr
EP3910262A4 (fr
Inventor
Kenta MURATA
Daisuke Ito
Takumi NISHIYAMA
Tsuyoshi Sato
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 EP3910262A1 publication Critical patent/EP3910262A1/fr
Publication of EP3910262A4 publication Critical patent/EP3910262A4/fr
Application granted granted Critical
Publication of EP3910262B1 publication Critical patent/EP3910262B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/06—Superheaters
    • 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
    • F28D7/10—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 being arranged one within the other, e.g. concentrically
    • F28D7/106—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 being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/09—Improving heat transfers
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles

Definitions

  • the present invention relates to a refrigeration cycle apparatus.
  • R32 refrigerant or R410A refrigerant has been conventionally used as refrigerant for a refrigeration cycle apparatus.
  • a refrigeration cycle apparatus in which R290 (propane) refrigerant having a global warming potential (GWP) smaller than that of R32 refrigerant or R410A refrigerant is used in a refrigerant circuit in order to reduce an influence on global warming.
  • GWP global warming potential
  • a refrigeration cycle apparatus including an internal heat exchanger for increasing a cooling capacity.
  • Japanese Patent Laying-Open No. 2008-164245 (PTL 1) describes a refrigeration cycle apparatus including propane as refrigerant for use in a refrigerant circuit and including an internal heat exchanger.
  • the refrigeration cycle apparatus described in this publication includes a compressor, a condenser, a heat exchanger, and an evaporator.
  • the heat exchanger corresponds to the internal heat exchanger.
  • the internal heat exchanger includes an inner pipe, and an outer pipe in which the inner pipe is inserted.
  • the refrigerant delivered from the compressor through the condenser to the internal heat exchanger is delivered to the evaporator through the inner pipe in the heat exchanger.
  • the refrigerant delivered to the evaporator returns to the compressor through the outer pipe in the internal heat exchanger.
  • PTL 2 discloses an internal heat exchanger having an outlet structure on the low pressure side thereof, wherein the outlet structure prevents a stagnation of oil in the internal heat exchanger.
  • PTL 3 discloses a refrigeration cycle apparatus comprising an accumulator and an internal heat exchanger, wherein the internal heat exchanger is formed in a spatial-bodily manner at its high pressure side or at its low-pressure side such that pulsations of passed through refrigerant are predominantly damped in pre-determined frequencies.
  • the present invention has been made in view of the above-described problem, and an object of the present invention is to provide a refrigeration cycle apparatus in which refrigerant having a small global warming potential can be used to increase a coefficient of performance of the refrigeration cycle apparatus and reduce an amount of the refrigerant in an internal heat exchanger.
  • a refrigeration cycle apparatus of the present invention inter alia includes: a refrigerant circuit; and refrigerant.
  • the refrigerant circuit inter alia includes a compressor, a condenser, an expansion valve, an evaporator, and an internal heat exchanger.
  • the refrigerant flows in the refrigerant circuit in order of the compressor, the condenser, the internal heat exchanger, the expansion valve, the evaporator, and the internal heat exchanger.
  • the refrigerant is a hydrocarbon refrigerant.
  • the internal heat exchanger includes: an inner pipe connected to the condenser and the expansion valve; and an outer pipe connected to the evaporator and the compressor, the inner pipe being inserted in the outer pipe.
  • the internal heat exchanger is configured to cause heat exchange between the refrigerant flowing inside the inner pipe in a direction from the condenser toward the expansion valve, and the refrigerant flowing inside the outer pipe and outside the inner pipe in a direction from the evaporator toward the compressor.
  • the refrigerant flowing inside the outer pipe and outside the inner pipe is entirely gas.
  • the refrigerant is a hydrocarbon refrigerant and the refrigerant flowing inside the outer pipe and outside the inner pipe of the internal heat exchanger is entirely gas. Therefore, the refrigerant having a small global warming potential can be used. In addition, a coefficient of performance of the refrigeration cycle apparatus can be increased. Furthermore, an amount of the refrigerant in the internal heat exchanger can be reduced.
  • FIG. 1 is a configuration diagram showing the refrigeration cycle apparatus according to the first embodiment of the present invention.
  • the refrigeration cycle apparatus according to the first embodiment of the present invention is, for example, an air conditioner.
  • refrigeration cycle apparatus 1 according to the first embodiment of the present invention inter alia includes a refrigerant circuit 2, a controller 3, a condenser fan 10, an evaporator fan 11, and refrigerant.
  • Refrigerant circuit 2 includes a compressor 4, a condenser 5, an expansion valve 6, an evaporator 7, and an internal heat exchanger 8. Compressor 4, condenser 5, expansion valve 6, evaporator 7, and internal heat exchanger 8 are connected by a pipe 9. Refrigerant circuit 2 is thus formed. Refrigerant circuit 2 is configured to circulate the refrigerant. Refrigerant circuit 2 is configured such that a refrigeration cycle is performed in which the refrigerant circulates in order of compressor 4, condenser 5, internal heat exchanger 8, expansion valve 6, evaporator 7, and internal heat exchanger 8 while changing its phase.
  • the refrigerant flows in refrigerant circuit 2 in order of compressor 4, condenser 5, internal heat exchanger 8, expansion valve 6, evaporator 7, and internal heat exchanger 8.
  • the refrigerant is such that a coefficient of performance of the refrigerant becomes higher as a suction superheat degree (suction SH) of compressor 4 becomes higher.
  • the refrigerant is propane (R290), isobutane (R600a), pentane (R601), butane (R600), ethane (R170), or propylene (R1270).
  • Controller 3 is configured to control refrigerant circuit 2. Controller 3 is configured to control instruments, devices and the like of refrigeration cycle apparatus 1 by performing computation, instruction and the like. Controller 3 is electrically connected to compressor 4, expansion valve 6, condenser fan 10, evaporator fan 11 and the like and is configured to control operations thereof.
  • Compressor 4 is configured to compress and discharge suctioned gaseous refrigerant.
  • Compressor 4 is configured to be capacity-variable.
  • Compressor 4 is configured such that a frequency is changed based on an instruction from controller 3 to thereby adjust a rotation speed and change a capacity.
  • refrigerator oil lubricating oil
  • the refrigerator oil is, for example, polyalkylene glycol (PAG)-based oil having an ether bond, polyol ester (POE)-based oil having an ester bond, or the like.
  • Condenser 5 is configured to condense the refrigerant compressed by compressor 4. Condenser 5 is connected to compressor 4 and internal heat exchanger 8. Condenser 5 includes a heat transfer tube through which the refrigerant flows. Condenser 5 is, for example, a fin-and-tube-type heat exchanger including a plurality of fins and a circular or flat heat transfer tube passing through the plurality of fins.
  • Expansion valve 6 is configured to expand and decompress the liquid refrigerant condensed by condenser 5.
  • the liquid refrigerant condensed by condenser 5 is expanded and decompressed by expansion valve 6, and thus, the refrigerant enters a gas-liquid two-phase state at an outlet of expansion valve 6.
  • Expansion valve 6 is connected to condenser 5 and evaporator 7.
  • Expansion valve 6 is, for example, an electric expansion valve configured to adjust a flow rate of the refrigerant based on an instruction from controller 3. An amount of the refrigerant flowing through expansion valve 6 is adjusted by adjusting a degree of opening of expansion valve 6.
  • Evaporator 7 is configured to evaporate the refrigerant decompressed by expansion valve 6.
  • Evaporator 7 is connected to expansion valve 6 and internal heat exchanger 8.
  • Evaporator 7 includes a heat transfer tube through which the refrigerant flows.
  • Evaporator 7 is, for example, a fin-and-tube-type heat exchanger including a plurality of fins and a circular or flat heat transfer tube passing through the plurality of fins.
  • Internal heat exchanger 8 is configured to cause heat exchange between the refrigerant on the outlet side of condenser 5 and the refrigerant on the outlet side of evaporator 7. In internal heat exchanger 8, heat exchange is performed between the refrigerant condensed by condenser 5 and the refrigerant evaporated by evaporator 7.
  • Pipe 9 connects compressor 4, condenser 5, expansion valve 6, evaporator 7, and internal heat exchanger 8.
  • Pipe 9 forms a gas-side refrigerant path and a liquid-side refrigerant path.
  • Pipe 9 includes a first pipe portion 9a, a second pipe portion 9b, a third pipe portion 9c, and a fourth pipe portion 9d.
  • First pipe portion 9a is connected to condenser 5 and internal heat exchanger 8.
  • Second pipe portion 9b is connected to internal heat exchanger 8 and expansion valve 6.
  • Third pipe portion 9c is connected to evaporator 7 and internal heat exchanger 8.
  • Fourth pipe portion 9d is connected to internal heat exchanger 8 and compressor 4.
  • condenser fan 10 is provided in a not-shown outdoor unit. Condenser fan 10 is configured to forcibly deliver outdoor air to condenser 5. Condenser fan 10 is attached to condenser 5 and is configured to supply air as a heat exchange fluid to condenser 5. Condenser fan 10 is configured such that a rotation speed of condenser fan 10 is adjusted based on an instruction from controller 3 to thereby adjust an amount of air flowing around condenser 5 and adjust an amount of heat exchange between the air and the refrigerant.
  • Evaporator fan 11 is provided in a not-shown indoor unit. Evaporator fan 11 is configured to forcibly deliver indoor air to evaporator 7. Evaporator fan 11 is attached to evaporator 7 and is configured to supply air as a heat exchange fluid to evaporator 7. Evaporator fan 11 is configured such that a rotation speed of evaporator fan 11 is adjusted based on an instruction from controller 3 to thereby adjust an amount of air flowing around evaporator 7 and adjust an amount of heat exchange between the air and the refrigerant.
  • internal heat exchanger 8 is a double-pipe-type heat exchanger.
  • Internal heat exchanger 8 includes an inner pipe 8a and an outer pipe 8b.
  • Inner pipe 8a has a pipe shape.
  • Outer pipe 8b has a pipe shape.
  • Inner pipe 8a is inserted in outer pipe 8b. That is, inner pipe 8a is arranged within outer pipe 8b.
  • a gap GP is provided between an outer circumferential surface of inner pipe 8a and an inner circumferential surface of outer pipe 8b. Gap GP may have an uniform dimension over an entire circumference in an outer circumferential direction of inner pipe 8a.
  • inner pipe 8a is connected to condenser 5 and expansion valve 6.
  • Inner pipe 8a is connected to condenser 5 with first pipe portion 9a being interposed, and is connected to expansion valve 6 with second pipe portion 9b being interposed.
  • Inner pipe 8a is configured such that the high-pressure-side refrigerant flows therethrough.
  • Outer pipe 8b is connected to evaporator 7 and compressor 4.
  • Outer pipe 8b is connected to evaporator 7 with third pipe portion 9c being interposed, and is connected to compressor 4 with fourth pipe portion 9d being interposed.
  • Outer pipe 8b is configured such that the low-pressure-side refrigerant flows therethrough.
  • Internal heat exchanger 8 is configured to cause heat exchange between the refrigerant flowing inside inner pipe 8a in a direction from condenser 5 toward expansion valve 6 and the refrigerant flowing inside outer pipe 8b and outside inner pipe 8a in a direction from evaporator 7 toward compressor 4.
  • Internal heat exchanger 8 is configured to cause heat exchange, via a wall surface of inner pipe 8a, between the refrigerant flowing inside inner pipe 8a and the refrigerant flowing inside outer pipe 8b and outside inner pipe 8a.
  • Internal heat exchanger 8 is configured to cause heat exchange, via the wall surface of inner pipe 8a, between the refrigerant flowing inside inner pipe 8a and the refrigerant flowing through gap GP.
  • the refrigerant flowing inside outer pipe 8b and outside inner pipe 8a is entirely gas.
  • the refrigerant flowing through gap GP is entirely gas.
  • the refrigerant flowing inside outer pipe 8b and outside inner pipe 8a is entirely in a dry state.
  • the gaseous refrigerant compressed by compressor 4 is discharged from compressor 4 and delivered to condenser 5 through pipe 9 serving as the gas-side refrigerant path.
  • condenser 5 heat is released from the refrigerant flowing through the heat transfer tube to the air, and the refrigerant is thereby condensed.
  • the refrigerant is delivered to internal heat exchanger 8 through first pipe portion 9a serving as the liquid-side refrigerant path.
  • the refrigerant delivered to internal heat exchanger 8 through first pipe portion 9a flows through inner pipe 8a of internal heat exchanger 8, and then, is delivered to expansion valve 6 through second pipe portion 9b.
  • expansion valve 6 the liquid refrigerant is decompressed to the refrigerant in a gas-liquid two-phase state.
  • the refrigerant decompressed by expansion valve 6 is delivered to evaporator 7 through pipe 9 serving as the liquid-side refrigerant path. Thereafter, the refrigerant takes in heat from the air and evaporates in evaporator 7, and then, is delivered to internal heat exchanger 8 through third pipe portion 9c serving as the gas-side refrigerant path.
  • the refrigerant delivered to internal heat exchanger 8 through third pipe portion 9c flows through outer pipe 8b of internal heat exchanger 8, and then, returns to compressor 4 through fourth pipe portion 9d.
  • internal heat exchanger 8 heat exchange is performed between the refrigerant on the outlet side of condenser 5 (high-pressure-side refrigerant) flowing through inner pipe 8a and the refrigerant on the outlet side of evaporator 7 (low-pressure-side refrigerant) flowing through outer pipe 8b. Since a degree of dryness of the refrigerant at the outlet of evaporator 7 can be reduced by internal heat exchanger 8, the heat transfer performance of evaporator 7 is improved. As a result, a coefficient of performance (COP) of refrigeration cycle apparatus 1 is improved.
  • COP coefficient of performance
  • the R290 refrigerant is used as one example of the refrigerant.
  • Comparative Example 1 is different from refrigeration cycle apparatus 1 according to the first embodiment of the present invention in that the refrigerant is R32.
  • the R32 refrigerant has a global warming potential (GWP) greater than that of the R290 refrigerant.
  • Comparative Example 1 is different from the refrigeration cycle apparatus according to the first embodiment of the present invention in that the low-pressure-side refrigerant flows through inner pipe 8a and the high-pressure-side refrigerant flows through outer pipe 8b in internal heat exchanger 8. That is, in Comparative Example 1, inner pipe 8a is connected to evaporator 7 and compressor 4 and outer pipe 8b is connected to condenser 5 and expansion valve 6 in internal heat exchanger 8.
  • Fig. 4 is a graph showing a relationship between a theoretical coefficient of performance (hereinafter, referred to as "theoretical COP") and a suction superheat degree (suction SH) of compressor 4 when each of the R290 refrigerant and the R32 refrigerant is used as the refrigerant for refrigerant circuit 2.
  • the coefficient of performance (COP) is a ratio of consumed electric power to a capacity of refrigeration cycle apparatus 1.
  • the theoretical COP of the R32 refrigerant decreases as the suction superheat degree (suction SH) of compressor 4 increases.
  • the theoretical COP of the R290 refrigerant increases as the suction superheat degree (SH) of compressor 4 increases. This is because the R290 refrigerant and the R32 refrigerant are different in properties. That is, as the suction superheat degree (suction SH) of compressor 4 increases, the coefficient of performance of the R290 refrigerant becomes superior to that of the R32 refrigerant.
  • the coefficient of performance of the R32 refrigerant is higher when the suction superheat degree (suction SH) of compressor 4 is zero than when the suction superheat degree (suction SH) of compressor 4 is higher than zero. Therefore, in order to increase the coefficient of performance, the low-pressure-side refrigerant is brought into a wet state in internal heat exchanger 8 so as to prevent the suction superheat degree (suction SH) of compressor 4 from becoming higher than zero.
  • Fig. 5 is a cross-sectional view showing a flowing state of the refrigerant in internal heat exchanger 8 in Comparative Example 1.
  • refrigerant R1 flowing through inner pipe 8a is low-pressure-side refrigerant
  • refrigerant R2 flowing through outer pipe 8b is high-pressure-side refrigerant.
  • Low-pressure-side refrigerant R1 flowing through inner pipe 8a is in a gas-liquid two-phase state.
  • Low-pressure-side refrigerant R1 flowing through inner pipe 8a forms an annular flow.
  • gas refrigerant Ra flows through a central portion of inner pipe 8a
  • liquid refrigerant Rb flows through an outer portion along the wall surface of inner pipe 8a. Since liquid refrigerant Rb comes into contact with the wall surface of inner pipe 8a serving as a heat transfer surface, the heat transfer performance increases.
  • the refrigerant in Comparative Example 1 is the R32 refrigerant
  • the global warming potential of the refrigerant is greater than that of the R290 refrigerant. Therefore, in Comparative Example 1, the global warming potential of the refrigerant cannot be reduced.
  • Fig. 6 is a cross-sectional view showing a flowing state of the refrigerant in internal heat exchanger 8 in Comparative Example 2.
  • refrigerant R1 flowing through inner pipe 8a is low-pressure-side refrigerant
  • refrigerant R2 flowing through outer pipe 8b is high-pressure-side refrigerant.
  • Comparative Example 2 is different from refrigeration cycle apparatus 1 according to the first embodiment of the present invention.
  • the refrigerant in Comparative Example 2 is propane (R290).
  • refrigerator oil 20 precipitated on the wall surface of inner pipe 8a of internal heat exchanger 8 serves as a thermal resistance, and thus, the heat transfer performance of internal heat exchanger 8 decreases.
  • Figs. 7 and 8 are cross-sectional views showing a flowing state of the refrigerant in internal heat exchanger 8 of refrigeration cycle apparatus 1 according to the first embodiment of the present invention.
  • refrigerant R1 flowing through inner pipe 8a is high-pressure-side refrigerant
  • refrigerant R2 flowing through outer pipe 8b is low-pressure-side refrigerant.
  • the wall surface of inner pipe 8a serves as a heat transfer surface where heat exchange is performed between high-pressure-side refrigerant R1 flowing through inner pipe 8a and low-pressure-side refrigerant R2 flowing through outer pipe 8b in internal heat exchanger 8.
  • the wall surface of inner pipe 8a serving as the heat transfer surface where heat exchange is performed between the low-pressure-side refrigerant flowing through outer pipe 8b and the high-pressure-side refrigerant flowing through inner pipe 8a
  • an area of the wall surface on which refrigerator oil 20 is precipitated is larger in refrigeration cycle apparatus 1 according to the first embodiment of the present invention than in Comparative Example 2.
  • an oil amount of the refrigerator oil precipitated on the wall surface of inner pipe 8a serving as the heat transfer surface decreases. Therefore, the refrigerator oil precipitated on the wall surface of inner pipe 8a serves as a thermal resistance, and thus, a reduction in heat transfer performance of internal heat exchanger 8 can be suppressed.
  • the propane (R290) refrigerant is used, and the high-pressure-side refrigerant flows through inner pipe 8a of internal heat exchanger 8 and the low-pressure-side refrigerant flows through outer pipe 8b of internal heat exchanger 8. Furthermore, the refrigerant at the low-pressure-side inlet of internal heat exchanger 8 is in a dry state. That is, the superheat degree of the refrigerant at the low-pressure-side inlet of internal heat exchanger 8 is zero. Therefore, a reduction in heat transfer performance caused by precipitation of the refrigerator oil in internal heat exchanger 8 is suppressed. Thus, the operation with a high coefficient of performance can be achieved in refrigeration cycle apparatus 1.
  • the refrigerant is a hydrocarbon refrigerant (HC refrigerant). Therefore, the refrigerant having a small global warming potential (GWP) can be used.
  • the refrigerant flowing inside outer pipe 8b and outside inner pipe 8a of internal heat exchanger 8 is entirely gas. Therefore, the superheat degree of the refrigerant at the inlet of compressor 4 can be increased, as compared with the case in which the refrigerant flowing inside outer pipe 8b and outside inner pipe 8a of internal heat exchanger 8 includes liquid refrigerant.
  • the coefficient of performance (COP) of refrigeration cycle apparatus 1 can be increased.
  • the superheat degree of the refrigerant at the outlet of outer pipe 8b of internal heat exchanger 8 can be increased, as compared with the case in which the refrigerant flowing inside outer pipe 8b and outside inner pipe 8a of internal heat exchanger 8 includes liquid refrigerant. Therefore, the amount of the refrigerant in internal heat exchanger 8 can be reduced.
  • the refrigerant is an HC refrigerant. Therefore, the global warming potential (GWP) of the refrigerant can be reduced.
  • GWP global warming potential
  • expansion valve 6 is an electric expansion valve configured to adjust a flow rate of the refrigerant. Therefore, the flow rate of the refrigerant can be adjusted by the electric expansion valve.
  • Refrigeration cycle apparatus 1 according to a second embodiment of the present invention has the same configuration, operation and effect as those of above-described refrigeration cycle apparatus 1 according to the first embodiment of the present invention, unless otherwise stated.
  • refrigeration cycle apparatus 1 according to the second embodiment of the present invention is different in a configuration of outer pipe 8b of internal heat exchanger 8 from refrigeration cycle apparatus 1 according to the first embodiment of the present invention.
  • a groove 30 is provided in an inner surface of outer pipe 8b of internal heat exchanger 8.
  • Groove 30 may be provided over an entire circumference of the inner surface of outer pipe 8b of internal heat exchanger 8.
  • Groove 30 may be configured to be serrated.
  • Inner pipe 8a of internal heat exchanger 8 is not provided with groove 30. That is, no groove is provided in an inner surface and an outer surface of inner pipe 8a of internal heat exchanger 8.
  • refrigerator oil 20 is likely to precipitate in groove 30, which is a portion that does not contribute to heat transfer between the refrigerant flowing through inner pipe 8a and the refrigerant flowing through outer pipe 8b in internal heat exchanger 8.
  • a reduction in heat transfer performance caused by the refrigerator oil precipitated on the wall surface of inner pipe 8a can be suppressed, as compared with the first embodiment.
  • groove 30 is provided in the inner surface of outer pipe 8b of internal heat exchanger 8. Since groove 30 results in an increase in heat transfer area of outer pipe 8b, refrigerator oil 20 is likely to precipitate in groove 30. Therefore, a reduction in heat transfer performance caused by the refrigerator oil precipitated on the wall surface of inner pipe 8a can be suppressed.
  • groove 30 is configured to be serrated. Therefore, the refrigerator oil is likely to precipitate on the bottom of the serrated configuration.
  • 1 refrigeration cycle apparatus 1 refrigeration cycle apparatus; 2 refrigerant circuit; 3 controller; 4 compressor; 5 condenser; 6 expansion valve; 7 evaporator; 8 internal heat exchanger; 8a inner pipe; 8b outer pipe; 9 pipe; 10 condenser fan; 11 evaporator fan; 20 refrigerator oil; 30 groove.

Landscapes

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

Claims (4)

  1. Appareil à cycle frigorifique (1), comprenant :
    un circuit frigorifique (2) comprenant un compresseur (4), un condenseur (5), un détendeur (6), un évaporateur (7) et un échangeur de chaleur interne (8) ;
    un dispositif de contrôle (3) ;
    un ventilateur de condenseur (10) ;
    un ventilateur d'évaporateur (11) ; et
    un fluide frigorigène approprié pour s'écouler dans le circuit frigorifique (2) dans l'ordre du compresseur (4), du condenseur (5), de l'échangeur de chaleur interne (8), du détendeur (6), de l'évaporateur (7) et de l'échangeur de chaleur interne (8),
    le fluide frigorigène étant un fluide frigorigène hydrocarboné qui est choisi dans le groupe comprenant le propane, l'isobutène, le pentane, le butane, l'éthane et le propylène,
    l'échangeur de chaleur interne (8) comprenant :
    un tuyau intérieur (8a) raccordé au condenseur (5) et au détendeur (6) ; et
    un tuyau extérieur (8b) raccordé à l'évaporateur (7) et au compresseur (4), le tuyau intérieur (8a) étant inséré dans le tuyau extérieur (8b),
    l'échangeur de chaleur interne (8) est configuré pour provoquer un échange de chaleur entre
    le réfrigérant circule à l'intérieur du tuyau intérieur (8a) dans une direction allant du condenseur (5) vers le détendeur (6), et
    le fluide frigorigène s'écoulant à l'intérieur du tuyau extérieur (8b) et à l'extérieur du tuyau intérieur (8a) dans une direction allant de l'évaporateur (7) vers le compresseur (4),
    dans lequel le dispositif de contrôle (3) est connecté électriquement au compresseur (4), au détendeur (6), au ventilateur de condenseur (10) et au ventilateur d'évaporateur (11) et est configuré pour contrôler leurs opérations de telle sorte que le fluide frigorigène s'écoulant à l'intérieur du tuyau extérieur (8b) et à l'extérieur du tuyau intérieur (8a) soit entièrement gazeux.
  2. Appareil à cycle frigorifique (1) selon la revendication 1, dans lequel une rainure (30) est prévue dans une surface intérieure du tuyau extérieur (8b).
  3. Appareil à cycle frigorifique (1) selon la revendication 2, dans lequel la rainure (30) présente une configuration dentelée.
  4. Appareil à cycle frigorifique (1) selon l'une quelconque des revendications 1 à 3, dans lequel le détendeur (6) est un détendeur électrique configurée pour ajuster un débit d'écoulement du fluide frigorigène.
EP19908451.8A 2019-01-09 2019-01-09 Dispositif à cycle de réfrigération Active EP3910262B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2019/000356 WO2020144764A1 (fr) 2019-01-09 2019-01-09 Dispositif à cycle de réfrigération

Publications (3)

Publication Number Publication Date
EP3910262A1 EP3910262A1 (fr) 2021-11-17
EP3910262A4 EP3910262A4 (fr) 2021-12-29
EP3910262B1 true EP3910262B1 (fr) 2024-08-21

Family

ID=71521528

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19908451.8A Active EP3910262B1 (fr) 2019-01-09 2019-01-09 Dispositif à cycle de réfrigération

Country Status (4)

Country Link
EP (1) EP3910262B1 (fr)
JP (1) JP7460550B2 (fr)
CN (1) CN113227672A (fr)
WO (1) WO2020144764A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN118541576A (zh) * 2022-01-21 2024-08-23 三菱电机株式会社 空调装置
TWI839240B (zh) * 2023-05-31 2024-04-11 台灣奧利安產業股份有限公司 流體熱交換系統
TWI841406B (zh) * 2023-05-31 2024-05-01 台灣奧利安產業股份有限公司 大氣熱交換系統
WO2025182020A1 (fr) * 2024-02-29 2025-09-04 三菱電機株式会社 Dispositif à cycle frigorifique

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4006861B2 (ja) * 1998-12-09 2007-11-14 株式会社デンソー 減圧器一体型熱交換器
DE19944951B4 (de) * 1999-09-20 2010-06-10 Behr Gmbh & Co. Kg Klimaanlage mit innerem Wärmeübertrager
JP2001280864A (ja) 2000-03-30 2001-10-10 Hitachi Ltd 熱交換器およびその製造方法
JP2003314927A (ja) * 2002-04-18 2003-11-06 Matsushita Electric Ind Co Ltd 熱交換器およびその熱交換器を用いた冷凍サイクル装置
JP2005009833A (ja) * 2003-06-20 2005-01-13 Hitachi Cable Ltd 二重管式熱交換器
JP2004012127A (ja) * 2003-10-02 2004-01-15 Mitsubishi Electric Corp 可燃性冷媒を用いた冷蔵庫
KR200420568Y1 (ko) * 2006-04-20 2006-07-04 주식회사 두원공조 내부열교환기의 저압측 출구 구조
JP2008164245A (ja) * 2006-12-28 2008-07-17 Kobelco & Materials Copper Tube Inc 熱交換器
JP4884365B2 (ja) 2007-12-28 2012-02-29 三菱電機株式会社 冷凍空調装置、冷凍空調装置の室外機および冷凍空調装置の制御装置
CN101363697A (zh) * 2008-09-28 2009-02-11 湖南晟通科技集团有限公司 一种具有微细通道结构的高效换热管
JP2010127498A (ja) * 2008-11-26 2010-06-10 Nippon Soken Inc 冷凍サイクル装置
JP2010261680A (ja) * 2009-05-11 2010-11-18 Sanden Corp 二重管式熱交換器
JP5504050B2 (ja) * 2009-06-30 2014-05-28 株式会社ケーヒン・サーマル・テクノロジー 二重管式熱交換器およびその製造方法
JP5333041B2 (ja) * 2009-08-21 2013-11-06 ダイキン工業株式会社 熱交換器及びそれを備えた冷凍装置
DE102013201313A1 (de) * 2012-02-23 2013-08-29 Ford Global Technologies, Llc Wärmetauscher für eine Klimaanlage
JP2014105890A (ja) * 2012-11-26 2014-06-09 Panasonic Corp 冷凍サイクル装置及びそれを備えた温水生成装置
JP5717903B2 (ja) * 2014-05-28 2015-05-13 三菱電機株式会社 冷凍空調装置

Also Published As

Publication number Publication date
WO2020144764A1 (fr) 2020-07-16
EP3910262A1 (fr) 2021-11-17
EP3910262A4 (fr) 2021-12-29
JP7460550B2 (ja) 2024-04-02
CN113227672A (zh) 2021-08-06
JPWO2020144764A1 (ja) 2021-09-30

Similar Documents

Publication Publication Date Title
JP6847299B2 (ja) 冷凍サイクル装置
EP3910262B1 (fr) Dispositif à cycle de réfrigération
US10101060B2 (en) Cooling system
EP3217115B1 (fr) Appareil de climatisation
KR101901540B1 (ko) 공기 조화 장치
EP3862651B1 (fr) Dispositif à cycle frigorifique
EP3483523A1 (fr) Appareil de cycle de réfrigération et appareil de climatisation équipé de celui-ci
US11371758B2 (en) Refrigeration cycle apparatus
JP6779383B2 (ja) 凝縮器および凝縮器を備えた冷凍装置
EP4184105A1 (fr) Échangeur de chaleur
JP2011214753A (ja) 冷凍装置
JP6758506B2 (ja) 空気調和装置
JP4078786B2 (ja) 冷凍空調サイクル装置
CN112012929A (zh) 压缩机润滑油质量管理
JP2014178110A (ja) 冷凍空調装置
JPWO2020188756A1 (ja) ルームエアコン
JP7154420B2 (ja) 冷凍サイクル装置
EP4467893A1 (fr) Climatiseur
CN113614481A (zh) 热交换器以及空调机
EP3770535A1 (fr) Échangeur de chaleur, dispositif à cycle frigorifique, et dispositif de climatisation
KR20220170108A (ko) 냉매 사이클을 구비하는 기기
EP4116642A1 (fr) Échangeur de chaleur et climatiseur
JP2002195700A (ja) 冷凍サイクル装置
EP4417900A1 (fr) Appareil de climatisation
JP2018194200A (ja) 冷凍サイクル装置およびそれを備えた液体循環装置

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

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

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20210503

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

A4 Supplementary search report drawn up and despatched

Effective date: 20211125

RIC1 Information provided on ipc code assigned before grant

Ipc: F28F 13/00 20060101ALI20211119BHEP

Ipc: F25B 40/06 20060101ALI20211119BHEP

Ipc: F25B 40/02 20060101ALI20211119BHEP

Ipc: F28D 7/10 20060101ALI20211119BHEP

Ipc: F25B 1/00 20060101AFI20211119BHEP

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
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: 20230323

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 13/18 20060101ALI20240306BHEP

Ipc: F28F 1/40 20060101ALI20240306BHEP

Ipc: F28D 21/00 20060101ALI20240306BHEP

Ipc: F28F 13/00 20060101ALI20240306BHEP

Ipc: F25B 40/06 20060101ALI20240306BHEP

Ipc: F25B 40/02 20060101ALI20240306BHEP

Ipc: F28D 7/10 20060101ALI20240306BHEP

Ipc: F25B 1/00 20060101AFI20240306BHEP

INTG Intention to grant announced

Effective date: 20240403

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: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602019057667

Country of ref document: DE

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20240821

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

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: 20241121

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1715835

Country of ref document: AT

Kind code of ref document: T

Effective date: 20240821

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: 20240821

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: 20241223

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: 20240821

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: 20241122

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: 20240821

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

Ref country code: GB

Payment date: 20241128

Year of fee payment: 7

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

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: 20240821

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

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: 20240821

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: 20240821

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: 20241221

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

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: 20240821

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

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: 20240821

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: 20241121

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

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: 20241121

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: 20241223

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: 20240821

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: 20241121

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: 20240821

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: 20240821

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: 20241221

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: 20240821

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: 20241122

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: 20240821

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: 20240821

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: 20240821

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: 20240821

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: 20240821

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: 20240821

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: 20240821

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

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: 20240821

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

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: 20240821

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: 20240821

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: 20240821

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602019057667

Country of ref document: DE

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

26N No opposition filed

Effective date: 20250522

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Ref country code: SE

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: 20240821

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: 20250109

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: 20240821

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

Free format text: CASE NUMBER: UPC_APP_4937_3910262/2025

Effective date: 20250827

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: 20250131

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

Ref country code: FR

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

Effective date: 20250131

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

Ref country code: CH

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

Effective date: 20250131

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20250131

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: 20250109

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

Ref country code: DE

Payment date: 20251203

Year of fee payment: 8