EP3070418A2 - Kälteanlage - Google Patents

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Publication number
EP3070418A2
EP3070418A2 EP16160865.8A EP16160865A EP3070418A2 EP 3070418 A2 EP3070418 A2 EP 3070418A2 EP 16160865 A EP16160865 A EP 16160865A EP 3070418 A2 EP3070418 A2 EP 3070418A2
Authority
EP
European Patent Office
Prior art keywords
fluid
heat exchanger
branch
inlet
refrigerant fluid
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.)
Granted
Application number
EP16160865.8A
Other languages
English (en)
French (fr)
Other versions
EP3070418B1 (de
EP3070418A3 (de
Inventor
Mauro Mantovan
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.)
Hiref SpA
Original Assignee
Hiref SpA
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Filing date
Publication date
Application filed by Hiref SpA filed Critical Hiref SpA
Publication of EP3070418A2 publication Critical patent/EP3070418A2/de
Publication of EP3070418A3 publication Critical patent/EP3070418A3/de
Application granted granted Critical
Publication of EP3070418B1 publication Critical patent/EP3070418B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with 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
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits

Definitions

  • the present patent application concerns an operating method and a reversible refrigeration circuit, in particular for a heat pump with cycle inversion with air condensation.
  • a heat pump comprises a reversible refrigeration circuit, which in turn comprises: a fin heat exchanger adapted to be installed in an outdoor environment; and a utility adapted to be installed inside a room to be conditioned.
  • the heat exchanger in turn comprises: manifolds; one or more heat exchange pipes which fluidly connect the manifolds to one another; and a plurality of fins which project radially, in a known way, from said heat exchange pipes.
  • the heat exchanger acts as a condenser or evaporator of the refrigeration cycle, according to the direction in which the refrigerant fluid flows through the inside of the refrigeration circuit.
  • the exchanger of known type as an evaporator (therefore supplying heat to the utility)
  • the refrigeration circuit has a low efficiency, especially when the heat exchanger is installed in an outdoor environment at low temperatures.
  • the outdoor temperatures can be extremely low and, due to the degree of relative humidity of the air, evaporation temperatures inside the heat exchanger can drop well below 0°C, frosting the humidity contained in the air on the surface of the heat exchanger fins.
  • the object of the present invention is to reduce, or even avoid, the formation of frost or ice on the fins of a heat exchanger installed outdoors, when the refrigeration circuit is used to heat the utility.
  • the object of the present invention is to provide an operating method and a refrigeration circuit which overcome the above-mentioned drawbacks.
  • the number 1 indicates as a whole a refrigeration circuit of a heat pump 2 which comprises:
  • thermal expansion valve 6 is a thermostatic valve of known type and illustrated schematically.
  • the switch 4 is of known type and illustrated schematically.
  • the switch 4 is connected, in a known way, both to the inlet I and to the delivery O of the compressor 3.
  • the refrigeration circuit 1 further comprises:
  • the heat pump 2 comprises:
  • the branch 8 comprises a non-return valve 16, which allows flow of the fluid F in the direction R1 from the switch 4 towards the exchanger 5.
  • the branch 9 comprises a non-return valve 17, which allows flow of the fluid F in the direction R1 from the exchanger 5 towards the thermal expansion valve 6.
  • the deviation branch 13 connects to the branch 9 downstream of the valve 17.
  • the deviation branch 12 comprises a non-return valve 18, which allows flow of the fluid F in the direction R2 from the exchanger 5 towards the compressor 3.
  • the branch 14 comprises a non-return valve 15, which allows flow of the fluid F in the direction R2 from the utility 7 towards the exchanger 5.
  • the deviation branch 13 comprises a non-return valve 19, which allows flow of the fluid F in the direction R2 from the utility 7 to the exchanger 5, a thermal expansion valve 20 and a distribution system 21, as will be illustrated in further detail below.
  • the thermal expansion valve 20 is arranged along the deviation branch 13 between the valve 19 and the distribution system 21.
  • the thermal expansion valve 20 is a thermostatic valve of known type and illustrated schematically.
  • the distribution system 21 comprises a distributor 22 (of known type and generally called Venturi gas distributor) and a plurality of capillary tubes 23, each of which has an end portion 24 and an end portion 25.
  • a distributor 22 of known type and generally called Venturi gas distributor
  • a plurality of capillary tubes 23 each of which has an end portion 24 and an end portion 25.
  • the distributor 22 comprises a body axially symmetrical and hollow inside, which has a substantially frustoconical shape, in particular having a narrowing, so as to create a Venturi effect inside it.
  • the distributor 22 has a plurality of radial openings (of known type and not illustrated); in each radial opening, an end portion 24 of a respective capillary tube 23 is engaged in a known way and is schematically illustrated.
  • the heat exchanger 5 is of the fin type, with a longitudinal axis L and is adapted to be lapped by an air flow according to the direction W substantially perpendicular to the axis L and illustrated in figure 3 .
  • the exchanger 5 comprises: a manifold assembly 27, a manifold assembly 28, a plurality of heat exchange pipes 40 substantially parallel to the axis L, each pipe 40 being bent so as to form coils with a plurality of sections parallel to one another, and a plurality of fins of known type and not illustrated. Substantially the fins are perpendicular to each heat exchange pipe 40.
  • the schematic block 29 represents a heat exchange unit of known type comprising heat exchange pipes 40 and fins.
  • the manifold assembly 27 comprises a manifold 30 having an internal cavity 31 and a longitudinal axis A substantially perpendicular to the axis L, an inlet 33, a plurality of pipes 34, which communicate with respective pipes 40 of the heat exchange unit 29, and a plurality of openings 32.
  • the pipes 34 are adapted to establish communication between the cavity 31 of the manifold 30 and the heat exchange pipes 40 (illustrated in figure 4 ) of the heat exchange unit 29.
  • the pipes 34 project from a longitudinal wall 36, which is opposite the wall 35. Each pipe 34 is adapted to establish communication between the cavity 31 and the outside.
  • the pipes 34 are substantially perpendicular to the axis A and are uniformly distributed along the axis A.
  • Each pipe 34 has an internal diameter adapted to house a respective capillary tube 23.
  • Each opening 32 is provided on the wall 35 and is arranged substantially at a respective pipe 34.
  • Each opening 32 has a diameter adapted to house a respective capillary tube 23.
  • an end portion 25 of a capillary tube 23 is arranged across the respective opening 32 and the cavity 31 of the manifold 30 and is inserted inside a respective pipe 34.
  • the capillary tubes 23 are tightly fixed on the wall 35 of the manifold 30.
  • each capillary tube 23 is braze-welded with the wall 35.
  • each pipe 34 and each capillary tube 23 define two inlets I1 and I2 feeding a respective pipe 40 of the heat exchanger 5.
  • the inputs I1 and I2 are distinct from each other and are configured to feed fluid F supplied by two different branches of the refrigeration circuit 1.
  • the inlet I1 is composed of the circular crown 51 delimited between a pipe 34 and the respective capillary tube 23.
  • the inlet I1 faces the inside of the cavity 31 of the manifold 30 and is configured to feed into the respective pipe 40 the fluid F in the form of superheated vapour Vss coming from the branch 8 when the fluid flows inside the refrigeration circuit 1 in the direction R1.
  • the inlet 12 is composed of the area 50 through which the capillary tube 23 passes.
  • the inlet 12 is configured to feed the fluid F in the liquid-vapour two-phase state Lv coming from the branch 13, through the feed system 21, when the fluid flows inside the refrigeration circuit 1 in the direction R2.
  • the heat exchanger 5 of the type described above has for each pipe 40 two inlets I1, I2 configured to feed fluid F coming from two different sources (from the branch 8 through the manifold 30 or from the branch 13 through the feed system 21) and in two different physical states.
  • the inlet 33 projects from a longitudinal wall 35 of the manifold 30 and is arranged in a substantially central position of the manifold 27.
  • the inlet 33 connects the cavity 31 with the outside.
  • the manifold assembly 28 is of known type and comprises a manifold 37 substantially parallel to the manifold 30 and an outlet 38, which is arranged at one end of the manifold 37.
  • the present solution is applicable both to systems with electromechanical type control and to systems with microprocessor control combined with appropriate control software.
  • the switch 4 is operated in a known way (manually or by traditional control means) so as to set the operating configuration of the refrigeration circuit 1 to cool or heat the utility 7.
  • the switch 4 directs the refrigerant flow F in the direction R1 inside the circuit 1.
  • the heat pump 2 During operation of the refrigeration circuit 1 to cool the utility 7, the heat pump 2 operates substantially like a traditional heat pump 2.
  • the flow F coming out of the compressor 3 in the state of superheated vapour Vss is conveyed to the exchanger 5 through the branch 8.
  • the superheated vapour Vss enters the manifold assembly 27 through the inlet 33 and flows, in a known way, through the pipes 40 of the exchanger 5 in a countercurrent flow relative to the direction W of the air flow, as illustrated in figure 4 .
  • the superheated vapour Vss condenses to obtain, at the outlet of said exchanger 5, substantially saturated liquid Ls, which is directed to the thermal expansion valve 6.
  • the fluid F in the saturated liquid state Ls passes to a liquid-vapour state Lv and is directed to the utility 7, which acts as an evaporator.
  • the fluid F in the liquid-vapour state Lv passes to the saturated vapour state Vs and is sent to the inlet I of the compressor 3 through the switch 4.
  • the switch 4 directs the refrigerant flow F in the direction R2 inside the refrigeration circuit 1.
  • the flow F coming out of the compressor 3 is in the state of superheated vapour Vss and is sent to the utility 7, which operates as a condenser.
  • the utility 7 Through the utility 7 the refrigerant fluid F passes to the saturated liquid state Ls. It is observed that in this operating configuration the thermal expansion valve 6 is closed and the saturated liquid Ls crosses the by-pass branch 14. Furthermore, the saturated liquid Ls is conveyed through the deviation branch 13 and across the thermal expansion valve 20.
  • the saturated liquid Ls passes to the liquid-vapour two-phase state Lv.
  • the distributor 21 the liquid-vapour Lv is uniformly distributed among all the capillary tubes 23, each of which conveys directly the liquid-vapour Lv inside a respective pipe 40.
  • each capillary tube 23 feeds the fluid F in the liquid-vapour two-phase state Lv into a respective pipe 40 through a respective inlet 12.
  • the fluid F in the liquid-vapour state Lv is uniformly distributed inside the exchanger 5 (in other words the fluid F in the liquid-vapour state is uniformly distributed among the pipes 40 of the heat exchanger 5), without the risk of the liquid separating from the vapour inside the manifold assembly 27 (which would inevitably lead to poor operation of the exchanger 5).
  • the fluid F in the liquid-vapour state Lv is fed into the exchanger 5 in a countercurrent flow relative to the direction W of the air thanks to the unit formed of: the deviation branch 13, the thermal expansion valve 20, the distributor 22 and the pipes 34.
  • the fluid F is transformed into saturated vapour Vs and is fed through the deviation branch 12 to the switch 4. Then, through the switch 4, the saturated vapour Vs is sent to the compressor 3.
  • the fluid F can be any type of refrigerant fluid commonly used in heat pumps.
  • the fluid F can be a fluid chosen from those indicated in the ASHRAE classification.
  • the refrigerant fluid F crosses the exchanger 5, again in a countercurrent flow relative to the direction W of the air.
  • the solution of the type described above always guarantees optimal operation and maximum performance of the heat exchanger 5 in any operating condition, minimizing in particular the negative effects of the flow of fluid F in the liquid-vapour state Lv thanks to the use of the double feed system of the pipes 40, and in particular to the use of the capillary tubes 23.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)
EP16160865.8A 2015-03-18 2016-03-17 Kälteanlage Active EP3070418B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ITBO20150132 2015-03-18

Publications (3)

Publication Number Publication Date
EP3070418A2 true EP3070418A2 (de) 2016-09-21
EP3070418A3 EP3070418A3 (de) 2017-01-11
EP3070418B1 EP3070418B1 (de) 2021-07-21

Family

ID=53284323

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16160865.8A Active EP3070418B1 (de) 2015-03-18 2016-03-17 Kälteanlage

Country Status (2)

Country Link
EP (1) EP3070418B1 (de)
ES (1) ES2881696T3 (de)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2279040A1 (fr) * 1974-07-17 1976-02-13 Bernier Jacques Pompes de chaleur a inversion de cycle
JPH0686969B2 (ja) * 1984-12-07 1994-11-02 株式会社日立製作所 空冷ヒ−トポンプ式冷凍サイクル
EP2500676B1 (de) * 2011-03-14 2019-07-03 STIEBEL ELTRON GmbH & Co. KG Wärmepumpe
WO2014155518A1 (ja) * 2013-03-26 2014-10-02 三菱電機株式会社 膨張弁及びこれを用いた冷凍サイクル装置

Non-Patent Citations (1)

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

Also Published As

Publication number Publication date
EP3070418B1 (de) 2021-07-21
EP3070418A3 (de) 2017-01-11
ES2881696T3 (es) 2021-11-30

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