EP3066406B1 - Pompe à chaleur pour un appareil ménager - Google Patents

Pompe à chaleur pour un appareil ménager Download PDF

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Publication number
EP3066406B1
EP3066406B1 EP14796292.2A EP14796292A EP3066406B1 EP 3066406 B1 EP3066406 B1 EP 3066406B1 EP 14796292 A EP14796292 A EP 14796292A EP 3066406 B1 EP3066406 B1 EP 3066406B1
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EP
European Patent Office
Prior art keywords
compressor
refrigerant
heat pump
condenser
tubes
Prior art date
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EP14796292.2A
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German (de)
English (en)
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EP3066406A1 (fr
Inventor
Francisco Barcelo Ruescas
Jose Gonzalvez Macia
Iñaki OTERO GARCIA
Roberto San Martin Sancho
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BSH Hausgeraete GmbH
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BSH Hausgeraete GmbH
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Priority claimed from EP20130382448 external-priority patent/EP2871432A1/fr
Application filed by BSH Hausgeraete GmbH filed Critical BSH Hausgeraete GmbH
Priority to PL14796292T priority Critical patent/PL3066406T3/pl
Priority to EP14796292.2A priority patent/EP3066406B1/fr
Publication of EP3066406A1 publication Critical patent/EP3066406A1/fr
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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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—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
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution

Definitions

  • the invention relates to a heat pump for a household appliance, in particular a laundry treatment appliance, comprising a compressor, a condenser, a restrictor, and an evaporator.
  • the invention further relates to a household appliance, in particular a laundry treatment appliance, comprising such heat pump.
  • a laundry dryer having a heat pump as specified typically comprises a refrigerant circuit and an air path.
  • the refrigerant circuit comprises the compressor, the condenser, the restrictor and the evaporator which are connected in series by refrigerant lines.
  • the refrigerant flows through the compressor, the condenser, the restrictor and the evaporator, in this order, and through the lines connecting these to one another.
  • the refrigerant releases heat to the process air as flowing through the air path by means of the condenser and extracts heat and humidity from the process air flowing through the air path by means of the evaporator.
  • the compressor converts mechanical power to thermal power by compressing the refrigerant in the refrigerant circuit.
  • process air flows from a drum to the evaporator.
  • the air is at a medium temperature and relatively wet.
  • the air is cooled and dehumidified and then flows to the condenser where it is heated. Hot and dry air is then introduced again into the drum where it absorbs moisture from laundry contained in the drum.
  • the evaporator and the condenser are thus acting as heat exchangers having a refrigerant side and a process air side.
  • EP-A-2644768 discloses a heat pump according to the preamble of claim 1.
  • the evaporator and the condenser may be of a tube-and-fins type.
  • the tubes of the evaporator and the condenser may be separate entities as described in prior art documents WO 2008/004802 A3 , EP 2 261 416 A1 , EP 2 244 044 A2 , EP 2 644 768 A1 , EP 2 418 448 A1 , WO 2013/153972 A1 , EP 2 468 948 A2 , and EP 1 593 770 B1 , or may be joined in a common core, as described in prior art document WO 2008/004802 A3 .
  • the tubes In frontal view parallel to the length of the tubes the tubes may be arranged in columns (or rows) each comprising several tubes. A distance between neighboring columns is called a 'longitudinal spacing', and a distance between neighboring tubes of one column is called a 'transversal spacing'.
  • Another typical construction of the evaporator and the condenser is the so-called aluminium single-tube type (no-frost type) in which an aluminium tube is bent and fins are placed along it without tube expansion.
  • An outer diameter of the tubes of the evaporator and the condenser used at present in a heat pump dryer are as follows: 3/8" (9.525 mm) and 7 mm for tube-and-fins type evaporators and condensers and 8 mm for aluminium single-tube type evaporator and condenser.
  • a laundry dryer comprising a heat pump has an improved efficiency (in terms of kWh/kg) as compared to a conventional laundry dryer only employing an electrical heater.
  • a related operational carbon dioxide emission of the laundry dryer comprising the heat pump is lower than that of a conventional dryer due to its lower electric consumption.
  • a refrigerant used in the heat pump must be taken into account with its GWP ('Global Warming Potential') which contributes to a total TEWI ('Total Equivalent Warming Impact') by direct or indirect emission of the refrigerant into the atmosphere.
  • GWP Global Warming Potential
  • TEWI Total Equivalent Warming Impact'
  • typical refrigerants used in a heat pump are fluorinated hydrocarbon compounds (HFC) whose GWP maybe as high as 1500, or even higher.
  • One possibility to reduce TEWI of these systems is to use hydrocarbon refrigerants that have low GWP like R-290 (propane) or R-1270 (propylene).
  • the main drawback of these refrigerants is that they are flammable and therefore IEC 60335-2-11 standard limits the maximum charge to 150 g of refrigerant in a laundry dryer. It is generally known that an optimum refrigerant charge can be found for a specific system, but the refrigerant limit of 150 g imposed by the IEC 60335-2-11 standard is typically lower than the optimum charge of refrigerant for a heat pump of a typical laundry dryer.
  • Efficiency is also affected by the compressor.
  • the efficiency of a rotary compressor is affected by different geometries of its components, including discharge and suction ports and rotor and cylinder geometries.
  • the variation of these geometries implies differences in mechanical frictions and in the thermodynamic behaviour of the refrigerant inside the compressor.
  • the losses in the compressor that determine its efficiency include the following: energy losses stemming from motor losses, friction losses, compression losses due to not ideal compression, valve losses due to gas pulsations and over-compression, and lubricant pumping losses, as well as mass flow losses stemming from clearance volume losses due to valve and cylinder head dimensions, leakage losses, back-flow-losses, suction gas heating losses due to a gas density at a cylinder inlet, and losses due to lubricant flow.
  • a heat pump for a household appliance in particular a laundry treatment appliance, comprising a compressor, a condenser, a restrictor, and an evaporator, that are connected in series by a refrigerant loop containing flammable refrigerant, wherein the condenser ('condenser coil') is of a tube-and-fin type with the tubes having an outer diameter of less than 7 mm.
  • This can even be achieved by having a quantity of flammable refrigerant of 150 grams or less within the heat pump.
  • the laundry treatment appliance may in particular be a laundry dryer.
  • the household appliance may also be a washing machine, a dishwasher, a cooling apparatus etc.
  • the condenser and the evaporator are typically arranged as heat exchangers, in particular refrigerant/air heat exchangers that are passed by process air of the household appliance.
  • the evaporator ('evaporator coil') is of a tube-and-fin type with the tubes having an outer diameter of 7 mm or less.
  • an outer diameter of the tubes of the condenser (“condenser coil”) is about 6 mm or less, in particular 5,5 mm or less, in particular 5 mm or less. It is another preferred embodiment that a transversal spacing of the tubes of the condenser is 21 mm or less while a longitudinal spacing is 19 mm or less. This leads to a higher heat transfer from a refrigerant side to an air side by means of: increasing a convection coefficient at the air side, creating a good balance between pressure losses and a size of a secondary surface at the air side, allowing a cooling down of the refrigerant even at low charge (i.e. a higher subcooling), and reaching a proper condensation pressure. It may be preferred that this is also holds for the evaporator coil and its tubes.
  • the roller of the compressor has a height-to-radius ratio of 1.4 to 1.2, in particular smaller than 1.4.
  • the roller is shaped as a hollow cylinder with the height measured along its longitudinal axis. The radius is typically measured perpendicular from the longitudinal axis to an outer diameter of the cylinder.
  • This embodiment reduces friction losses and therefore increases the efficiency of the compressor by achiev ing the same cooling capacity with a lower power input.
  • a height-to-radius ratio of current rollers of rotary compressors used laundry dryers is between 1.7 and 1.5. It is a particular variant of the compressor according to the invention that the height-to-radius ratio is between 1.4 and 1.2.
  • an area of a discharge port of the compressor, in particular rotary compressor is 19.8 mm 2 (square millimeters) or higher. This also achieves an increased efficiency of the compressor (same cooling capacity with a lower power input) and by reducing a pressure drop in a discharge valve.
  • a displacement of the compressor is between 6 cc (cubic centimeters) and 9.5 cc. If the compressor displacement is bigger than 9.5 cc it might be required to increase a heating capacity at the condenser in order to enable proper dissipation of energy pumped from compressor. This would mean a higher condenser area and volume. This in turn, would require an increase in refrigerant charge in order to allow the condensation of the refrigerant in the condenser which is not desired due to the dryer safety standard limitation of 150 g for flammable refrigerants. If the compressor displacement is lower than 6 cc then the refrigerant mass flow rate will decrease so much that an energy transfer in the heat exchangers is negatively affected.
  • an oil quantity within the compressor is between 150 cc and 210 cc for improved performance. Particularly preferred is an oil quantity equal or less than 180 cc.
  • the oil in the compressor has a reduced solubility with the refrigerant, wherein the solubility is lower than 35%. This in particular holds at a working point of the heat pump dryer at a pressure of about 26 bar (e.g. 26 +/- 0.5 bar) with a condensation pressure at 70°C) and a mix temperature of the oil and e.g. R290 of 80°C.
  • a proper combination of oil type and quantity of it increases the amount of available refrigerant in the heat exchangers and assures a good lubrication and internal leakage sealing at the compressor providing good volumetric efficiency.
  • This embodiment makes use of the fact that the main amount of the refrigerant of the heat pump is located in the condenser coil (because of a high inner volume of its coil and a relatively high density of the refrigerant) and in the compressor (where the refrigerant is mixed with oil). The refrigerant inside the compressor that is mixed with oil is not available in the heat exchangers for energy transfer purpose.
  • the less refrigerant is mixed with oil inside the compressor the higher is the amount of refrigerant within the heat exchangers.
  • This in turn leads to the effects that subcooling is increased to maintaining constant the superheating, that the dehumidification rate is increased (due to a higher difference of enthalpy in the evaporator) and that a reduction of compressor power consumption is expected due to lower friction losses and therefore an increase of compressor efficiency (i.e. the same cooling capacity with lower power input).
  • the oil preferably has a kinematic viscosity.
  • a mixture viscosity between 1.5 mm2/s (cSt) and 4 mm2/s is preferred, in particular at the heat pump dryer working point.
  • the heat pump dryer working point may e.g. have a pressure of about 26 bar (having a condensation pressure at 70°C) and a mix temperature of oil and R290 of 80°C. That range of viscosity with higher values than previously used oils is preferred in order to assure good internal leakage sealing in the compressor (which is particularly preferred due to low density of R290) and therefore to improve compressor volumetric efficiency.
  • These high values of kinematic viscosity lead to higher friction losses (negative effect in compressor efficiency).
  • the overall situation is that the compressor efficiency is improved when oils with high kinematic viscosity are used.
  • PAG Polyalkylene Glycols
  • POE Polyolester Oils
  • the values refer to working parameters of the heat pump dryer at its working point, namely a pressure of about 26 bar (having a condensation pressure at 70°C and a mix temperature with R290, for example, of 80°C).
  • These oils have the advantage that they exhibit an advantageous value of oil kinematic viscosity that is preferred in order to assure good internal leakage sealing in order to improve compressor volumetric efficiency and therefore improve compressor efficiency.
  • They have the additional advantage that they have a relatively low solubility with the refrigerant compared to other typically used oils of the same types, like POE RB-68EP in heat pump dryer compressors.
  • Table1 shows a comparison among different oils mixed with R290 under the above mentioned conditions: Oil Mass of R290 in the mixture (%) Refrigerant mass in mixture (g) Mixture viscosity (mm2/s or cSt) PZ46M 18 32.08 2.7 PZ100S 30 53.46 3.8 POE RB-68EP 27 48.36 1.12 POE RB-P68EP 24 42.98 1.6 NM80EP 30 48.60 1.2 EXP-4437 33 59.10 0.45
  • a refrigerant of the vapour compression system of the heat pump is a flammable refrigerant, in particular R290 (propane).
  • R290 propane
  • any other suitable flammable refrigerant may be used, e.g. R-1270 (propylene).
  • propane is used as a refrigerant in conjunction with a condenser coil of the tube-and-fins type with the tubes having an outer diameter of 5 mm.
  • the evaporator coil is also of the tube-and-fins type with the tubes having an outer diameter of 7 mm.
  • the rotary compressor has a displacement smaller than 9.5 cc and higher than 6 cc.
  • the compressor comprises a roller having a height-to-radius ration between 1.40 and 1.20.
  • An area of the discharge port of the compressor is larger than 19.8 mm2.
  • a quantity of oil in the compressor is between 150cc and 210cc.
  • the type of oil is PAG PZ100S from Idemitsu Kosan Co., Ltd. (or an equivalent); the type of oil is POE RB-P68EP from JX Nippon Oil & Energy Corporation (or an equivalent).
  • the transversal spacing of the tubes of the condenser coil is less than 21 mm while the longitudinal spacing is less than 19 mm. It is particularly preferred that the transversal spacing of the tubes of the condenser coil is about 19 mm (e.g. 19.05 mm) while the longitudinal spacing is about 16.5 mm.
  • the object of the invention is also achieved by a household appliance comprising the heat pump as described above.
  • the laundry treatment appliance may in particular be a laundry dryer, e.g. as a stand-alone apparatus or as a washing/drying combination.
  • the household appliance may also be a washing machine, a dishwasher, a cooling apparatus etc.
  • the invention allows using vapour compression or heat pump laundry dryers with hydrocarbons or any other flammable fluid as refrigerant having a low charge and a high efficiency.
  • Conventional solutions use a high volume in the refrigerant circuit (known solutions use 9.52 mm, 8 mm or 7 mm outer tube diameter heat exchangers with refrigerant loads higher than 190 g) and a high quantity of oil which has a high solubility with the refrigerant.
  • IEC 60335-2-11 of 150 g for flammable refrigerants it is not possible for the conventional solutions to have enough subcooling.
  • Fig.1 shows a laundry treatment appliance in form of a household tumble dryer H.
  • the tumble dryer H comprises a heat pump P having at least a compressor 1, a condenser 2 of a tube-and-fins type, a restrictor 3, and an evaporator 4 of a tube-and-fins type as elements.
  • the elements 1 to 4 are serially connected in the shown order by refrigerant pipes 5 to form a refrigerant circuit or path.
  • the tumble dryer H also comprises a process air circuit or path 6 wherein process air A flows.
  • the air circuit 6 comprises a rotatable drum 7 for holding laundry to be processed.
  • the air A leaves the drum 7 at a medium temperature and wet.
  • the air A then flows to the evaporator 4 that is placed in the air circuit A downstream the drum 7 and works as a heat exchanger.
  • the air A is cooled down and condenses.
  • the resultant condensate is collected in a water tank W.
  • the air A also cools down and transfers part of its thermal energy upon the evaporator 4 and thus onto the refrigerant R within the evaporator 4. This enables the evaporator 4 to transform the refrigerant R from a liquid state into a vaporous state.
  • the now dry and cool air A passes through the condenser 2 where a heat transfer from the condenser 2 and the refrigerant R, resp., to the air A is effected to heat up the air A and cool down the refrigerant R to its liquid state.
  • the then warm and dehumidified / dry air A is subsequently reintroduced into the drum 7 to warm up the clothes and to pick up moisture.
  • the refrigerant R is moved within the refrigerant circuit 1 to 5 by the compressor 1.
  • the refrigerant R is a flammable refrigerant, in particularly R290. An amount of the flammable refrigerant R is 150 g or less.
  • the evaporator 4 and the condenser 2 are thus used as heat exchangers.
  • Fig.2 shows a sectional top view onto a condenser 2 of the expanded tube and fins type.
  • the condenser 2 comprises five hairpin tubes 8 of basically the same 'U'-shape that have the same orientation and are aligned in the same direction.
  • the hairpin tubes 8 are shown in the same plane for the sake of simplicity, they are generally arranged in a three-dimensional structure.
  • the hairpin tubes 8 are mechanically and thermally connected to a connection structure formed by a stack of fins 9. At its frontal side F and its rearward side B, the stack of fins 9 is covered by a respective end plate 10 for mechanical protection. Straight legs 11 of the hairpin tubes 8 penetrate the fins 9 in a perpendicular fashion.
  • the bends or bent sections 12 of the hairpin tubes 8 are all situated on one side of the stack of fins 9 while (open) ends 13 of the hairpin tubes 8 are all situated on the other side of the stack of fins 9.
  • the stack of fins 9 provides stiffness to the condenser 2 and restricts relative movement of the hairpin tubes 8.
  • the stack of fins 9 restricts or dampens a propagation of externally induced forces and movements to elements of the condenser 2.
  • the hairpin tubes 8 are connected to form an open-ended fluid channel. To this effect, the hairpin tubes 8 are connected in pairs such that intermediate hairpin tubes 8 are connected to a respective hairpin tube 8 on both ends 13 and two terminal (or terminally located) hairpin tubes 8 are each connected to an intermediate hairpin tube 8 on only one end 13. The other end 13 of each terminal hairpin tube 8 is not connected to a hairpin tube 8 but to respective refrigerant lines 5.
  • connection between the hairpin tubes 8 is effected using tubes in form of tube elbows 14 that are bent 180° ('U'-shaped or 'C'-shaped pipe elbows 14).
  • the tube elbows 14 are attached to the open ends 13 of the hairpin tubes 8 e.g. by brazing or soldering, in particular flame brazing or flame soldering, to achieve a particularly durable, compact and cost-effective connection.
  • the hairpin tubes 8 and/or tube elbows 14 may be made of the same material, e.g. aluminium or copper. Alternatively, as indicated, the hairpin tubes 8 and/or tube elbows 14 may be made of different materials, e.g. aluminium (shown without hatching) and copper (shown with hatching).
  • the hairpin tubes 8 and/or tube elbows 14 have an outer diameter of 7 mm of less, practically neglecting possible expanded end sections where hairpin tubes 8 and tube elbows 14 are stuck together.
  • the hairpin tubes 8 and/or tube elbows 14 have an outer diameter dc of 5 mm.
  • a meander-like condenser coil 8, 14 of a tube-and-fin type is formed.
  • flammable refrigerant R e.g. R290
  • R290 may be introduced into and discharged from the condenser coil 8, 14 as indicated by the straight arrows.
  • Fig.3A shows a frontal view of the condenser 2 of Fig.2 in the direction F of Fig.2 onto the condenser 2, now showing eight instead of five the hairpin tubes 8.
  • the frontally projecting 'U' shaped or 'C' shaped pipe elbows 14 of outer diameter dc of 5 mm are depicted as shown in Fig.3B while the hairpin tubes 8 of outer diameter dc of 5 mm with their rearward projecting bent sections 12 are depicted as shown in Fig.3C .
  • the hairpin tubes 8 and/or tube elbows 14 may again be made of different materials, e.g. aluminium (shown without hatching) and copper (shown with hatching).
  • the condenser 2 has a three-dimensional structure for good thermal exchange and for easy placement in the tumble dryer H.
  • the straight legs 11 of the hairpin tubes 8 are arranged in parallel columns C. Neighbouring columns C have a longitudinal distance or spacing dL of 19 mm or less. A transversal distance or spacing dT between neighbouring straight legs 11 of the same column C is 21 mm or less. In particular, a transversal spacing dT is 19.05 mm and a longitudinal spacing dL is 16.5 mm.
  • the hairpin tubes 8 and/or tube elbows 14 of an evaporator coil may preferably have a larger outer diameter than those of the condenser coil 8, 14, e.g. 7 mm.
  • Fig.4 shows a top view onto an opened rotary compressor 1 of the household tumble dryer H.
  • Fig.5 shows a cross-sectional side view of the opened rotary compressor of Fig.4 .
  • the compressor 1 comprises an outer cylinder 15 with a cavity 15a which houses a cylindrical roller 16.
  • the roller 16 is supported by an end face 17 of the outer cylinder 15.
  • the roller 16 can move or slip along the end face 17.
  • a longitudinal axis L1 of the outer cylinder 15 and a longitudinal axis L2 of the roller 16 are aligned in parallel but spaced apart.
  • the roller 16 is rollingly rotated within the outer cylinder 15 by a shaft 18 that is connected to an electrical motor (not shown).
  • the shaft 18 lies concentric to the outer cylinder 15 and is thus eccentric to the roller 16.
  • the shaft 18 has a laterally positioned cam 19 (only shown in Fig.5 ) that presses the roller 16 onto an inner side wall 20 of the outer cylinder 15.
  • the roller 16 thus has a contact point K with the inner side wall 20.
  • a path of the contact point K at the inner side wall 20 then describes a closed ring.
  • a displacement of the compressor 1 for one full rotation is between 6 cc and 9.5 cc.
  • the shaft 18 is formed as a hollow cylinder such that is can be connected to an oil pump (not shown) to feed oil into the compressor 1.
  • the oil quantity within the compressor 1 is between 150 cc and 210 cc, preferably 180 cc or less.
  • the oil may in particular be PAG PZ100S with 100 cSt or POE RB-P68EP with 68 cSt or an equivalent.
  • the outer cylinder 15 Into the cavity 15a of the outer cylinder 15 protrudes a blade 21.
  • the outer cylinder 15 also has a suction port 22 leading through its wall to suck refrigerant into the cavity 15a and a discharge port 23 leading through the end face 17 to discharge the refrigerant.
  • An area Q of the discharge port 23 is 19.8 mm 2 or higher, preferably larger than 19.8 mm 2 , preferably 20 mm 2 or larger, preferably 21 mm 2 or larger.
  • a cover lid (not shown) is put onto the open side of the outer cylinder 15.
  • the cover lid may have a bushing for the shaft 18.
  • a shown ratio of a height h to a radius r to an outer face of the roller 16 (the 'height-to-radius ratio' is between 1.4 and 1.2, preferably less than 1.4.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Detail Structures Of Washing Machines And Dryers (AREA)
  • Accessory Of Washing/Drying Machine, Commercial Washing/Drying Machine, Other Washing/Drying Machine (AREA)

Claims (10)

  1. Pompe à chaleur (P) pour un appareil ménager (H), comprenant un compresseur rotatif (1) avec un galet (16), un condensateur (2), un limiteur (3) et un évaporateur (4), dans laquelle le condensateur (2) est de type étendu à tubes et ailettes, les tubes (11) présentant un diamètre extérieur (dc) inférieur à 7 mm, dans lequel le réfrigérant de la pompe à chaleur (P) est un réfrigérant inflammable, en particulier le R290,
    caractérisée en ce que
    - le galet (16) revêt la forme d'un cylindre creux possédant, entre sa hauteur et son rayon externe, un ratio de 1,4 à 1,2, et
    - une quantité d'huile à l'intérieur du compresseur (1) possède une solubilité avec le réfrigérant inférieure à 35%.
  2. Pompe à chaleur (P) selon la revendication 1, dans laquelle un espacement transversal (dT) des tubes (11) du condensateur (2) est de 21 mm ou moins et un espacement longitudinal (dL) est de 19 mm ou moins.
  3. Pompe à chaleur (P) selon l'une quelconque des revendications précédentes, dans laquelle une surface (Q) de l'orifice de refoulement (23) est de 19,8 mm2 ou plus.
  4. Pompe à chaleur (P) selon l'une quelconque des revendications précédentes, dans laquelle une cylindrée du compresseur (1) se situe entre 6 cc et 9,5 cc.
  5. Pompe à chaleur (P) selon l'une quelconque des revendications précédentes, dans laquelle une quantité d'huile à l'intérieur du compresseur (1) se situe entre 150 cc et 210 cc.
  6. Pompe à chaleur (P) selon l'une quelconque des revendications précédentes, dans laquelle un type d'huile à l'intérieur du compresseur (1) correspond à : PAG PZ100S et/ou POE RB-P68EP.
  7. Pompe à chaleur (P) selon l'une quelconque des revendications précédentes, dans laquelle
    - le condensateur (2) est de type étendu à tubes et ailettes, les tubes (11) possédant un diamètre extérieur (dc) de 5 mm,
    - un espacement transversal (dT) des tubes (11) du condensateur (2) est inférieur à 21 mm et un espacement longitudinal (dL) est inférieur à 19 mm.
    - un serpentin évaporateur est de type étendu à tubes et ailettes, les tubes possédant un diamètre extérieur de 7 mm,
    - le compresseur (1) possède une cylindrée inférieure à 9,5 cc et supérieure à 6 cc,
    - une surface (Q) d'un orifice de refoulement (23) du compresseur (1) est supérieure à 19,8 mm2,
    - une quantité d'huile dans le compresseur (1) se situe entre 150cc et 210cc.
  8. Pompe à chaleur (P) selon la revendication 7, dans laquelle un espacement transversal (dT) des tubes (11) du condensateur (2) est d'environ 19 mm et un espacement longitudinal (dL) est d'environ 16,5 mm.
  9. Appareil ménager (H) comprenant la pompe à chaleur (P) selon l'une quelconque des revendications précédentes.
  10. Appareil ménager (h) selon la revendication 9, prenant la forme d'un appareil de traitement du linge.
EP14796292.2A 2013-11-06 2014-11-03 Pompe à chaleur pour un appareil ménager Active EP3066406B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PL14796292T PL3066406T3 (pl) 2013-11-06 2014-11-03 Pompa ciepła do urządzenia gospodarstwa domowego
EP14796292.2A EP3066406B1 (fr) 2013-11-06 2014-11-03 Pompe à chaleur pour un appareil ménager

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP20130382448 EP2871432A1 (fr) 2013-11-06 2013-11-06 Pompe à chaleur pour un appareil ménager
ES201331628 2013-11-06
EP14796292.2A EP3066406B1 (fr) 2013-11-06 2014-11-03 Pompe à chaleur pour un appareil ménager
PCT/IB2014/065759 WO2015068092A1 (fr) 2013-11-06 2014-11-03 Pompe à chaleur destinée à un appareil ménager

Publications (2)

Publication Number Publication Date
EP3066406A1 EP3066406A1 (fr) 2016-09-14
EP3066406B1 true EP3066406B1 (fr) 2018-01-10

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Application Number Title Priority Date Filing Date
EP14796292.2A Active EP3066406B1 (fr) 2013-11-06 2014-11-03 Pompe à chaleur pour un appareil ménager

Country Status (5)

Country Link
EP (1) EP3066406B1 (fr)
CN (1) CN105705899A (fr)
ES (1) ES2659046T3 (fr)
PL (1) PL3066406T3 (fr)
WO (1) WO2015068092A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3617388A1 (fr) 2018-08-30 2020-03-04 Electrolux Appliances Aktiebolag Sèche-linge comprenant un système de pompe à chaleur
EP3617389A1 (fr) 2018-08-30 2020-03-04 Electrolux Appliances Aktiebolag Sèche-linge comprenant un système de pompe à chaleur
EP3617391A1 (fr) 2018-08-30 2020-03-04 Electrolux Appliances Aktiebolag Sèche-linge comprenant un système de pompe à chaleur
EP3617392A1 (fr) 2018-08-30 2020-03-04 Electrolux Appliances Aktiebolag Sèche-linge comprenant un système de pompe à chaleur
EP3617390A1 (fr) 2018-08-30 2020-03-04 Electrolux Appliances Aktiebolag Sèche-linge comprenant un système de pompe à chaleur
EP3617393A1 (fr) 2018-08-30 2020-03-04 Electrolux Appliances Aktiebolag Sèche-linge comprenant un système de pompe à chaleur
EP4411141A3 (fr) * 2019-06-28 2024-10-23 LG Electronics Inc. Compresseur pour un appareil de traitement du linge

Families Citing this family (6)

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Publication number Priority date Publication date Assignee Title
EP3382315B1 (fr) 2017-03-31 2019-11-20 BSH Hausgeräte GmbH Sèche-linge comprenant au moins un échangeur de chaleur à tubes et ailettes
EP3388571B1 (fr) 2017-04-10 2020-07-29 BSH Hausgeräte GmbH Appareil de séchage de vêtements
CN116949777A (zh) * 2019-08-14 2023-10-27 Lg电子株式会社 衣物烘干机
EP3896210A1 (fr) * 2020-04-15 2021-10-20 Electrolux Appliances Aktiebolag Appareil de traitement du linge comprenant un système de pompe à chaleur
EP3896213A1 (fr) * 2020-04-15 2021-10-20 Electrolux Appliances Aktiebolag Appareil de traitement du linge comprenant un système de pompe à chaleur
EP3896211A1 (fr) * 2020-04-15 2021-10-20 Electrolux Appliances Aktiebolag Appareil de traitement de linge comprenant un système de pompe à chaleur

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JP4286712B2 (ja) 2004-05-06 2009-07-01 パナソニック株式会社 衣類乾燥機
JP4266903B2 (ja) 2004-09-07 2009-05-27 三洋電機株式会社 洗濯乾燥機
KR101265605B1 (ko) 2006-07-04 2013-05-22 엘지전자 주식회사 의류 처리 장치
DE102008043920A1 (de) 2008-11-20 2010-05-27 BSH Bosch und Siemens Hausgeräte GmbH Kondensationstrockner mit einer Wärmepumpe sowie Verfahren zu seinem Betrieb
DE102008055087A1 (de) 2008-12-22 2010-06-24 BSH Bosch und Siemens Hausgeräte GmbH Trockner mit Wärmepumpe und Umluftanteil sowie Verfahren zu seinem Betrieb
ES2385767B1 (es) 2009-04-15 2013-06-17 Bsh Electrodomesticos España S.A. Licuador así como también bomba de calor y aparato doméstico con un licuador de tal tipo.
EP2261416B1 (fr) 2009-06-09 2013-02-20 Electrolux Home Products Corporation N.V. Échangeur de chaleur pour séchoir, spécialement pour un séchoir domestique
WO2011016452A1 (fr) * 2009-08-06 2011-02-10 ダイキン工業株式会社 Compresseur
DE102009055206A1 (de) 2009-12-22 2011-06-30 BSH Bosch und Siemens Hausgeräte GmbH, 81739 Hausgerät mit Wärmepumpenkreislauf
EP2418448A1 (fr) * 2010-08-09 2012-02-15 BSH Electrodomésticos España, S.A. Échangeur de chaleur, appareil domestique, procédé de fabrication d'un échangeur de chaleur et procédé d'installation d'un échangeur de chaleur
EP2455526A1 (fr) 2010-11-17 2012-05-23 BSH Bosch und Siemens Hausgeräte GmbH Machine comportant une pompe à chaleur et ensemble de procédés correspondant
EP2468948B1 (fr) * 2010-12-21 2013-11-27 Panasonic Corporation Appareil de chauffage/déshumidification et sèche-linge l'utilisant
DE102011081022A1 (de) 2011-08-16 2013-02-21 BSH Bosch und Siemens Hausgeräte GmbH Wäschetrocknungsgerät mit einer Wärmepumpe umfassend einen Antrieb sowie Verfahren zu seinem Betrieb
DE102011085468A1 (de) 2011-10-28 2013-05-02 BSH Bosch und Siemens Hausgeräte GmbH Wäschetrocknungsgerät mit einer Wärmepumpe und einem Antrieb der Wärmepumpe
EP2644768A1 (fr) * 2012-03-30 2013-10-02 BSH Electrodomésticos España, S.A. Pompe à chaleur pour appareil de traitement de linge
WO2013153972A1 (fr) 2012-04-13 2013-10-17 古河スカイ株式会社 Tube d'échange de chaleur attaché avec une rainure interne d'alliage d'aluminium

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3617388A1 (fr) 2018-08-30 2020-03-04 Electrolux Appliances Aktiebolag Sèche-linge comprenant un système de pompe à chaleur
EP3617389A1 (fr) 2018-08-30 2020-03-04 Electrolux Appliances Aktiebolag Sèche-linge comprenant un système de pompe à chaleur
EP3617391A1 (fr) 2018-08-30 2020-03-04 Electrolux Appliances Aktiebolag Sèche-linge comprenant un système de pompe à chaleur
EP3617392A1 (fr) 2018-08-30 2020-03-04 Electrolux Appliances Aktiebolag Sèche-linge comprenant un système de pompe à chaleur
EP3617390A1 (fr) 2018-08-30 2020-03-04 Electrolux Appliances Aktiebolag Sèche-linge comprenant un système de pompe à chaleur
EP3617393A1 (fr) 2018-08-30 2020-03-04 Electrolux Appliances Aktiebolag Sèche-linge comprenant un système de pompe à chaleur
EP4411141A3 (fr) * 2019-06-28 2024-10-23 LG Electronics Inc. Compresseur pour un appareil de traitement du linge

Also Published As

Publication number Publication date
ES2659046T3 (es) 2018-03-13
CN105705899A (zh) 2016-06-22
PL3066406T3 (pl) 2018-07-31
EP3066406A1 (fr) 2016-09-14
WO2015068092A1 (fr) 2015-05-14

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