EP2831330A1 - Heat pump for a clothes treatment appliance, and clothes treatment appliance comprising such heat pump - Google Patents

Heat pump for a clothes treatment appliance, and clothes treatment appliance comprising such heat pump

Info

Publication number
EP2831330A1
EP2831330A1 EP13720601.7A EP13720601A EP2831330A1 EP 2831330 A1 EP2831330 A1 EP 2831330A1 EP 13720601 A EP13720601 A EP 13720601A EP 2831330 A1 EP2831330 A1 EP 2831330A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
heat pump
refrigerant line
condenser
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.)
Granted
Application number
EP13720601.7A
Other languages
German (de)
French (fr)
Other versions
EP2831330B1 (en
Inventor
Jose Gonzalvez Macia
Iñaki OTERO GARCIA
Roberto San Martin Sancho
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.)
BSH Hausgeraete GmbH
Original Assignee
BSH Bosch und Siemens Hausgeraete GmbH
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
Priority claimed from EP12382127.4A external-priority patent/EP2644768A1/en
Application filed by BSH Bosch und Siemens Hausgeraete GmbH filed Critical BSH Bosch und Siemens Hausgeraete GmbH
Priority to EP13720601.7A priority Critical patent/EP2831330B1/en
Publication of EP2831330A1 publication Critical patent/EP2831330A1/en
Application granted granted Critical
Publication of EP2831330B1 publication Critical patent/EP2831330B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00—Domestic laundry dryers
    • D06F58/20—General details of domestic laundry dryers 
    • D06F58/206—Heat pump arrangements

Definitions

  • the invention relates to a heat pump for a clothes treatment appliance, comprising a compressor, a condenser, a restrictor, and an evaporator, and further comprising a liquid- suction heat interchanger, wherein the liquid-suction heat interchanger comprises a first refrigerant line and a second refrigerant line that are thermally coupled to each other; an inlet of the first refrigerant line of the heat interchanger is coupled to an outlet of the evaporator and an outlet of the first refrigerant line is coupled to an inlet of the compres- sor; and an inlet of the second refrigerant line is coupled to an outlet of the condenser and an outlet of the second refrigerant line is coupled to an inlet of the restrictor.
  • the invention also relates to a clothes treatment appliance comprising such heat pump.
  • a heat pump and a clothes treatment appliance comprising such heat pump are disclosed in EP 2 385 169 A1.
  • an additional heat exchanger for exchanging heat between a flow of ambient air and refrigerant exiting from the condenser, and for exchanging heat between refrigerant exiting from the condenser and refrigerant exiting from the evaporator is provided.
  • That heat exchanger includes an additional interaction between the heat pump and its ambient into the operation of the heat pump which makes operation of the heat pump considerably more difficult to handle. Variations of ambient temperature result in variations of the operating condition of the heat pump.
  • a laundry dryer comprising a heat pump has 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 the 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').
  • typical refrigerants used in a heat pump are fluorinated hydrocarbon compounds (HFC) whose GWP is higher than 1500.
  • 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 in the drum where it can absorb moisture from laundry contained in the drum.
  • the evaporator and the condenser are typically 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 , and EP 1 593 770 B1 , or may be joined in the same core, as described in prior art document WO 2008/004802 A3.
  • alumin- ium single-tube type (no-frost type) in which an aluminium tube is bended 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 heat pump dryers are as follows: 3/8" (9.525mm) and 7 mm for a tube-and-fins type evaporator and condenser and 8 mm for an aluminium single-tube type evaporator and condenser.
  • TEWI Total Equivalent Warming Impact', that includes direct and indirect emission
  • hydrocarbon refrigerants that have a low GWP like R-290 (propane) or R-1270 (propylene).
  • R-290 propane
  • R-1270 propylene
  • IEC 60335-2-1 1 standard limits the maximum charge (150g) 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 60335-2-1 1 standard is typically lower than the optimum charge of refrigerant for a heat pump of a laundry dryer.
  • a clothes drying appliance having a heat pump typically comprises a refrigerant circuit and an air path.
  • the refrigerant flows through the compressor, the condenser, the restrictor and the evaporator, in this order. These elements are connected by refrigerant lines, in particular pipes.
  • the refrigerant releases heat to the process air flowing through the air path by means of the condenser and absorbs heat and humidity from the process air flowing through the air path by means of the evaporator.
  • the compressor absorbs power and compresses the refrigerant in the refrigerant circuit.
  • a liquid-suction heat interchanger (also called a liquid-to-suction heat exchanger or regenerator) is mainly known in low temperature refrigeration systems using a vapour compression system where there is a long distance between the evaporator and the compressor.
  • the liquid-suction heat interchanger typically comprises two refrigerant lines or channels (e.g. pipes), wherein in one of the refrigerant lines (the 'liquid' line) flows liquid refrigerant and in the other refrigerant line (the 'suction' line) flows refrigerant in its vaporous form.
  • the lines are thermally connected to each other to allow a heat transfer between them and are typically thermally isolated against the environment.
  • the liquid- suction heat interchanger may increase cooling capacity and reduce power input in vapour compression systems for some refrigerants.
  • the liquid- suction heat interchanger may work with evaporation temperatures below zero degrees centigrade (corresponding to an evaporator outlet temperature of around -20°C). Therefore, an external superheating (between the refrigerant and an ambient air) is created in the suction line due to a high temperature difference. This external superheating degrades the heat pump's COP (coefficient of performance; cooling capacity divided by power input) because the compressor power consumption is increased with no effect on the cooling capacity.
  • COP coefficient of performance; cooling capacity divided by power input
  • a heat pump for a clothes treatment appliance comprising a compressor, a condenser, a restrictor, and an evaporator, and further comprising a liquid- suction heat interchanger
  • the liquid-suction heat interchanger comprises a first refrigerant line and a second refrigerant line that are thermally coupled to each other; an inlet of the first refrigerant line of the heat interchanger is coupled to an outlet of the evaporator and an outlet of the first refrigerant line is coupled to an inlet of the compres- sor; and an inlet of the second refrigerant line is coupled to an outlet of the condenser and an outlet of the second refrigerant line is coupled to an inlet of the restrictor.
  • the first refrigerant line and the second refrigerant line are thermally isolated against an environment of the liquid-suction heat interchanger.
  • a clothes treatment appliance comprising a heat pump, wherein the heat pump is a heat pump as described above.
  • a further advantage is that the refrigerant mass flow may be decreased. Therefore a temperature of the refrigerant at the compressor inlet is increased due to extra superheating in the liquid-suction heat interchanger. Thus, a density of the refrigerant at the compressor inlet is lowered which leads to a decrease of a power consumption of the compressor.
  • the heat pump comprising the liquid-suction heat interchanger is working in its optimum operation point (showing superheating in the evaporator)
  • the cooling capacity in the evaporator is increased (since the effect of an enthalpy increase is bigger than that of a mass flow decrease) and the power consumption is reduced to achieve the same com- pression ratio.
  • a dehumidification rate is increased with a reduction of the power consumption. This means that a drying time and an energy consumption of the drying cycle are reduced. Also, an increase in cooling capacity in the evaporator improves the COP, especially for hydrocarbon refrigerants.
  • one side of the first refrigerant line (suction line) of the heat interchanger is coupled to an outlet of the evaporator and the other side of the first refrigerant line is coupled to an inlet of the compressor; and further one side of the second refrigerant line (liquid line) is coupled to an outlet of the condenser and the other side of the second refrigerant line is coupled to an inlet of the restrictor.
  • this kind of connection allows the heat interchanger to cool down refrigerant from the condenser outlet (giving more subcooling) and to heat up the evaporator outlet (giving more superheat).
  • the heat pump of the heat interchanger may use a flammable or non-flammable refriger- ant.
  • the heat interchanger can be of different configurations (e.g. as a double pipe, as a plate heat exchanger and so on). It is a preferred embodiment of the invention that the second (liquid) refrigerant line is thermally more isolated against the ambient than the first (suction) refrigerant line. This preserves the temperature increase at the compressor inlet.
  • this design may be implemented by using the first pipe as the first (suction) refrigerant line and using the second pipe as the second (liquid) refrigerant pipe.
  • the vaporous refrigerant flowing in the first pipe experiences a lower temperature difference to the environment while the liquid refrigerant flowing in the second pipe experiences a higher temperature difference since it is thermally shielded against the environment by the first pipe.
  • the compressor exhibits a displacement of 12 cc/rev (cubic centimeters per revolution) or less, in particular 10.5 cc/rev or less. This embodiment reflects the surprising finding that if the compressor displacement is bigger (in particular for typical household appliances), it might be required to increase a heating capacity at the condenser in order to enable a dissipation of energy coming from the compressor.
  • an outer diameter of the condenser pipes i.e. pipes used with a condenser
  • an outer diameter of the evaporator pipes i.e. pipes used with n evaporator
  • the use of the outer diameter being smaller than 7 mm is preferred in order to enable the condensation of the refrigerant in the condenser (using a smaller refrigerant charge in the condenser).
  • an outer diameter of the con- denser pipes measures less than 7 mm while an outer diameter of the evaporator pipes measures 7 mm or more, e.g. 3/8" (9.525mm) or 7 mm for a tube-and-fins type evaporator and 8 mm for an aluminium single-tube type evaporator.
  • This embodiment makes use of the fact that the refrigerant line of the condenser (also called condenser coil) is the part of the refrigerant circuit which has the highest inner volume and consequently the highest amount of refrigerant (i.e. a higher volume and a higher density of the refrigerant).
  • the inner volume is decreased, so for the same mass of refrigerant a higher density is obtained.
  • a larger percentage of liquid refrigerant in liquid-vapour phase is obtained which in turn allows a sooner condensation of the refrigerant in the condenser.
  • a higher subcooling is achieved with the consequent benefit for the cooling capacity.
  • an outer diameter of the condenser pipes and/or an outer diameter of the evaporator pipes is about 6 mm or less, in particular 5 mm or less.
  • An outer diameter of about 5 mm has been found to be a particularly good compromise between a small charge of the refrigerant and a high efficiency.
  • the combination of a 5 mm condenser and a 5 mm evaporator may bring an additional improvement as compared to the reference case of a 7 mm condenser (and 7 mm evaporator).
  • the use of the 5 mm condenser and the 5 mm evaporator brings a dry- ing time reduction of 16% and an energy consumption reduction of 14%.
  • a refrigerant of the heat pump is a flammable refrigerant.
  • This embodiment is made practical by enabling a charge of the refrigerant of 150g or less.
  • Flammable refrigerant often has a lower GWP than non- flammable refrigerant.
  • the refrigerant comprises a hydrocarbon refrigerant or a plurality of hydrocarbon refrigerants.
  • Hydrocarbon refrigerants show a low to negligible GWP. Hydrocarbon refrigerants are particularly useful to be used in the liquid-suction heat interchanger to improve system COP.
  • the refrigerant is or comprises propane (R290).
  • propane has the advantage to have a relatively low GWP (of 3.3 times the GWP of carbon dioxide), does not destroy the ozone layer, may be used as an alternative to R-12, R-22, R-134a and other chlorinated and/or fluorinated hydrocarbons, and is readily available.
  • the refrigerant is or comprises propylene (R1270).
  • the refrigerant is or comprises HFO-1234yf or 2,3,3,3-Tetra- fluoropropene.
  • HFO-1234yf has almost no environmental impact, acquiring a GWP rating 335 times less than that of the conventional R-134a and an atmospheric lifetime of about 400 times shorter. Furthermore, HFO-1234yf is only mildly flammable.
  • the clothes treatment appliance is a clothes drying appliance, e.g. a stand-alone clothes dryer or a washer-dryer. It is another preferred embodiment of the invention that the clothes treatment appliance is a household appliance.
  • Fig.1 shows a schematic drawing of a household tumble dryer using a heat pump
  • Fig.2 shows a schematic drawing of a heat pump of the tumble dryer
  • Fig.3 shows a sectional side view of a liquid-suction heat interchanger of the heat pump.
  • Fig.1 shows a clothes 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 to be processed clothes.
  • 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.
  • 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 within 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 working of such a tumble dryer H with its heat pump P (comprising the refrigerant circuit 1 to 5) and its air circuit 6 is well known and does not need to be explained in greater detail.
  • Fig.2 shows a schematic drawing of a heat pump P'.
  • the heat pump P' may be used in the tumble dryer H instead of the heat pump P.
  • the heat pump P' differs from heat pump P in that it comprises a liquid-suction heat interchanger 8.
  • the heat interchanger 8 is of a double pipe design and comprises a first refrigerant line 9 in form of a tubular (suction) pipe 9 having a suction pipe inlet 9i for inputting low pressure refrigerant R and a suction pipe outlet 9o for outputting the vaporous refrigerant R.
  • a second refrigerant line 10 in form of a tubular (liquid) pipe 10 having a liquid pipe inlet 10i for inputting high pressure refrigerant R and a liquid pipe outlet 10o for outputting the liquid refrigerant R at a respective end.
  • the suction pipe 9 and the liquid pipe 10 are highly thermally con- nected, e.g.
  • the suction pipe 9 may be thermally less isolated against its environment than the liquid pipe 10.
  • the suction pipe inlet 9i is coupled to an outlet 4o of the evaporator 4 via a refrigerant pipe 5
  • the suction pipe outlet 9o is coupled to an inlet 1 i of the compressor 1 via another refrigerant pipe 5.
  • the liquid pipe inlet 10i of the liquid pipe 10 is coupled to an outlet 2o of the condenser 2 and the liquid pipe outlet 10o is coupled to an inlet 3i of the restrictor 3.
  • This kind of connection allows the heat interchanger 8 to cool down refrig- erant R from the condenser outlet 2o (giving a stronger subcooling) and to heat up the evaporator outlet 4o (giving a stronger superheating).
  • the compressor 1 of the heat pump P' exhibits a displacement lower than 10.5 cc/rev.
  • the outer diameter of the tube or pipe of the tube-and-fins type condenser 2 is 5 mm.
  • the outer diameter of the tube or pipe of the evaporator 4 may also be 5 mm.
  • the refrigerant R is or comprises propane, propylene and/or HFO-1234yf.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Detail Structures Of Washing Machines And Dryers (AREA)
  • Drying Of Solid Materials (AREA)

Abstract

The invention relates to a heat pump P' for a clothes treatment appliance H. The heat pump P' comprises a compressor 1, a condenser 2, a restrictor 3, and an evaporator 4, and further comprises a liquid-suction heat interchanger 8. The liquid-suction heat interchanger 8 comprises a first refrigerant line 9 and a second refrigerant line 10 that are thermally coupled to each other. An inlet 9i of the first refrigerant line 9 of the heat interchanger 8 is coupled to an outlet 4o of the evaporator 4, and an outlet 9o of the first refrigerant line 9 is coupled to an inlet 1 i of the compressor 1. An inlet 10i of the second refrigerant line 10 is coupled to an outlet 2o of the condenser 2 and an outlet 10omicron of the second refrigerant line 10 is coupled to an inlet 3i of the restrictor 3. The first refrigerant line 9 and the second refrigerant line 10 are thermally isolated against an environment of the liquid-suction heat interchanger 8. A clothes treatment appliance H according to the invention comprises such heat pump P'.

Description

Heat Pump for a Clothes Treatment Appliance, and Clothes Treatment Appliance comprising such Heat Pump
The invention relates to a heat pump for a clothes treatment appliance, comprising a compressor, a condenser, a restrictor, and an evaporator, and further comprising a liquid- suction heat interchanger, wherein the liquid-suction heat interchanger comprises a first refrigerant line and a second refrigerant line that are thermally coupled to each other; an inlet of the first refrigerant line of the heat interchanger is coupled to an outlet of the evaporator and an outlet of the first refrigerant line is coupled to an inlet of the compres- sor; and an inlet of the second refrigerant line is coupled to an outlet of the condenser and an outlet of the second refrigerant line is coupled to an inlet of the restrictor. The invention also relates to a clothes treatment appliance comprising such heat pump.
A heat pump and a clothes treatment appliance comprising such heat pump are disclosed in EP 2 385 169 A1. In the heat pump disclosed therein, an additional heat exchanger for exchanging heat between a flow of ambient air and refrigerant exiting from the condenser, and for exchanging heat between refrigerant exiting from the condenser and refrigerant exiting from the evaporator is provided. That heat exchanger includes an additional interaction between the heat pump and its ambient into the operation of the heat pump which makes operation of the heat pump considerably more difficult to handle. Variations of ambient temperature result in variations of the operating condition of the heat pump.
A laundry dryer comprising a heat pump has improved efficiency (in terms of kWh/kg) as compared to a conventional laundry dryer only employing an electrical heater. Thus, in principle a related operational carbon dioxide emission of the laundry dryer comprising the heat pump is lower than that of the conventional dryer due to its lower electric consumption. However, a refrigerant used in the heat pump must be taken into account with its GWP ('Global Warming Potential'). Nowadays, typical refrigerants used in a heat pump are fluorinated hydrocarbon compounds (HFC) whose GWP is higher than 1500.
Within the air path or process air circuit; process air flows from a drum to the evaporator. At a drum outlet, the air is at a medium temperature and relatively wet. At the evaporator, the air is cooled and dehumidified and then flows to the condenser where it is heated. Hot and dry air is then introduced again in the drum where it can absorb moisture from laundry contained in the drum.
The evaporator and the condenser are typically 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 , and EP 1 593 770 B1 , or may be joined in the same core, as described in prior art document WO 2008/004802 A3.
Another typical construction of the evaporator and the condenser is the so-called alumin- ium single-tube type (no-frost type) in which an aluminium tube is bended 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 heat pump dryers are as follows: 3/8" (9.525mm) and 7 mm for a tube-and-fins type evaporator and condenser and 8 mm for an aluminium single-tube type evaporator and condenser.
One possibility to reduce TEWI (Total Equivalent Warming Impact', that includes direct and indirect emission) of these systems is to use hydrocarbon refrigerants that have a low GWP like R-290 (propane) or R-1270 (propylene). The main drawback of these refrigerants is that they are flammable and therefore IEC 60335-2-1 1 standard limits the maximum charge (150g) 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 60335-2-1 1 standard is typically lower than the optimum charge of refrigerant for a heat pump of a laundry dryer.
A clothes drying appliance having a heat pump typically comprises a refrigerant circuit and an air path. The refrigerant flows through the compressor, the condenser, the restrictor and the evaporator, in this order. These elements are connected by refrigerant lines, in particular pipes. The refrigerant releases heat to the process air flowing through the air path by means of the condenser and absorbs heat and humidity from the process air flowing through the air path by means of the evaporator. The compressor absorbs power and compresses the refrigerant in the refrigerant circuit. A liquid-suction heat interchanger (also called a liquid-to-suction heat exchanger or regenerator) is mainly known in low temperature refrigeration systems using a vapour compression system where there is a long distance between the evaporator and the compressor. The liquid-suction heat interchanger typically comprises two refrigerant lines or channels (e.g. pipes), wherein in one of the refrigerant lines (the 'liquid' line) flows liquid refrigerant and in the other refrigerant line (the 'suction' line) flows refrigerant in its vaporous form. The lines are thermally connected to each other to allow a heat transfer between them and are typically thermally isolated against the environment. The liquid- suction heat interchanger may increase cooling capacity and reduce power input in vapour compression systems for some refrigerants. For refrigeration systems the liquid- suction heat interchanger may work with evaporation temperatures below zero degrees centigrade (corresponding to an evaporator outlet temperature of around -20°C). Therefore, an external superheating (between the refrigerant and an ambient air) is created in the suction line due to a high temperature difference. This external superheating degrades the heat pump's COP (coefficient of performance; cooling capacity divided by power input) because the compressor power consumption is increased with no effect on the cooling capacity. Liquid-suction heat interchangers are only rarely used in air conditioning systems because the liquid-suction heat interchanger introduces a pressure drop that significantly reduces its benefits for an air conditioning system.
It is an object of the current invention to at least partially overcome at least some of the problems of the art with respect to clothes treatment appliances comprising a heat pump and to particularly provide a heat pump for a clothes treatment appliance that has a reduced GWP and a high efficiency.
The object is achieved by the features of the independent claims. Preferred embodiments are particularly referred to by the dependent claims.
The object is achieved by a heat pump for a clothes treatment appliance, comprising a compressor, a condenser, a restrictor, and an evaporator, and further comprising a liquid- suction heat interchanger, wherein the liquid-suction heat interchanger comprises a first refrigerant line and a second refrigerant line that are thermally coupled to each other; an inlet of the first refrigerant line of the heat interchanger is coupled to an outlet of the evaporator and an outlet of the first refrigerant line is coupled to an inlet of the compres- sor; and an inlet of the second refrigerant line is coupled to an outlet of the condenser and an outlet of the second refrigerant line is coupled to an inlet of the restrictor. In addition, the first refrigerant line and the second refrigerant line are thermally isolated against an environment of the liquid-suction heat interchanger.
The object is also achieved by a clothes treatment appliance comprising a heat pump, wherein the heat pump is a heat pump as described above.
The additional use of a liquid-suction heat interchanger in a clothes treatment appliance gives the advantage of a potential increase of the enthalpy in the evaporator (in particular at a refrigerant inlet of the evaporator) by exchanging heat between portions of refrigerant in different sections of the heat pump. This measure relates to internal parameters of the heat pump only and avoids any substantial interaction with the ambient of the heat pump. The result is an increase in stability and reliability of operation even under changes in per- tinent parameters of the ambient.
A further advantage is that the refrigerant mass flow may be decreased. Therefore a temperature of the refrigerant at the compressor inlet is increased due to extra superheating in the liquid-suction heat interchanger. Thus, a density of the refrigerant at the compressor inlet is lowered which leads to a decrease of a power consumption of the compressor. In particular, if the heat pump comprising the liquid-suction heat interchanger is working in its optimum operation point (showing superheating in the evaporator), the cooling capacity in the evaporator is increased (since the effect of an enthalpy increase is bigger than that of a mass flow decrease) and the power consumption is reduced to achieve the same com- pression ratio. It follows that a dehumidification rate is increased with a reduction of the power consumption. This means that a drying time and an energy consumption of the drying cycle are reduced. Also, an increase in cooling capacity in the evaporator improves the COP, especially for hydrocarbon refrigerants. Yet another advantage is that one side of the first refrigerant line (suction line) of the heat interchanger is coupled to an outlet of the evaporator and the other side of the first refrigerant line is coupled to an inlet of the compressor; and further one side of the second refrigerant line (liquid line) is coupled to an outlet of the condenser and the other side of the second refrigerant line is coupled to an inlet of the restrictor. In particular this kind of connection allows the heat interchanger to cool down refrigerant from the condenser outlet (giving more subcooling) and to heat up the evaporator outlet (giving more superheat).
The heat pump of the heat interchanger may use a flammable or non-flammable refriger- ant.
The heat interchanger can be of different configurations (e.g. as a double pipe, as a plate heat exchanger and so on). It is a preferred embodiment of the invention that the second (liquid) refrigerant line is thermally more isolated against the ambient than the first (suction) refrigerant line. This preserves the temperature increase at the compressor inlet. In case of a double pipe design (in which a first pipe surrounds a second pipe) this design may be implemented by using the first pipe as the first (suction) refrigerant line and using the second pipe as the second (liquid) refrigerant pipe. Thus, the vaporous refrigerant flowing in the first pipe experiences a lower temperature difference to the environment while the liquid refrigerant flowing in the second pipe experiences a higher temperature difference since it is thermally shielded against the environment by the first pipe. It is another preferred embodiment of the invention that the compressor exhibits a displacement of 12 cc/rev (cubic centimeters per revolution) or less, in particular 10.5 cc/rev or less. This embodiment reflects the surprising finding that if the compressor displacement is bigger (in particular for typical household appliances), it might be required to increase a heating capacity at the condenser in order to enable a dissipation of energy coming from the compressor. To increase condenser capacity, in turn, necessitates a higher condenser area and volume. Therefore, it would be required to also increase the refrigerant charge in order to enable the condensation of the refrigerant in the condenser. This, however, makes it difficult comply with the charge limit (150g) for flammable refrigerants of the IEC 60335-2-1 1 standard and might shift an optimum charge for an operat- ing point of the heat pump further away from the (present) 150g limit.
It is yet another preferred embodiment of the invention that an outer diameter of the condenser pipes (i.e. pipes used with a condenser) and/or an outer diameter of the evaporator pipes (i.e. pipes used with n evaporator) measures less than 7 mm. This reduces a refrigerant circuit volume and allows to effectively cool the refrigerant even at a low charge (in particular of less than 150g) while by virtue of the liquid-suction heat interchanger an efficiency of the heat pump remains high. In particular, the use of the outer diameter being smaller than 7 mm is preferred in order to enable the condensation of the refrigerant in the condenser (using a smaller refrigerant charge in the condenser). Thus, two positive effects can be achieved at the same time: the increase of subcooling in the condenser and the proper efficiency of liquid-to-suction heat exchanger (additional subcooling on the high pressure side and additional superheating on the low pressure side). In practice, lines (and pipes in particular) are measured and characterized by their outer diameter which correlates to its inner diameter and thus to the volume available for the refrigerant.
It is a particularly preferred embodiment of the invention hat an outer diameter of the con- denser pipes measures less than 7 mm while an outer diameter of the evaporator pipes measures 7 mm or more, e.g. 3/8" (9.525mm) or 7 mm for a tube-and-fins type evaporator and 8 mm for an aluminium single-tube type evaporator. This embodiment makes use of the fact that the refrigerant line of the condenser (also called condenser coil) is the part of the refrigerant circuit which has the highest inner volume and consequently the highest amount of refrigerant (i.e. a higher volume and a higher density of the refrigerant). With the use of the outer diameter smaller than 7 mm, the inner volume is decreased, so for the same mass of refrigerant a higher density is obtained. This in turn means that a larger percentage of liquid refrigerant in liquid-vapour phase is obtained which in turn allows a sooner condensation of the refrigerant in the condenser. Thus, a higher subcooling is achieved with the consequent benefit for the cooling capacity.
It is another particularly preferred embodiment that an outer diameter of the condenser pipes and/or an outer diameter of the evaporator pipes is about 6 mm or less, in particular 5 mm or less. An outer diameter of about 5 mm has been found to be a particularly good compromise between a small charge of the refrigerant and a high efficiency.
As a concrete example a comparison between a conventional 7 mm condenser (i.e. a condenser with a refrigerant pipe having an outer diameter of 7 mm) and a 5 mm condenser of a household tumble dryer using 150g of propane, also known as R290, is con- sidered. These 5 mm condenser has a 12% lower volume of the refrigerant than the 7 mm condenser. The 5 mm condenser achieves a drying time reduction of 13% and an energy consumption reduction of 1 1 %. In order to achieve a similar dryer performance using the 7 mm condenser and employing the same drying time and a 4% higher energy consump- tion, 21 Og of R290 is needed.
Furthermore, the combination of a 5 mm condenser and a 5 mm evaporator may bring an additional improvement as compared to the reference case of a 7 mm condenser (and 7 mm evaporator). The use of the 5 mm condenser and the 5 mm evaporator brings a dry- ing time reduction of 16% and an energy consumption reduction of 14%.
It is even another preferred embodiment of the invention that a refrigerant of the heat pump is a flammable refrigerant. This embodiment is made practical by enabling a charge of the refrigerant of 150g or less. Flammable refrigerant often has a lower GWP than non- flammable refrigerant.
It is still another preferred embodiment thereof that the refrigerant comprises a hydrocarbon refrigerant or a plurality of hydrocarbon refrigerants. Hydrocarbon refrigerants show a low to negligible GWP. Hydrocarbon refrigerants are particularly useful to be used in the liquid-suction heat interchanger to improve system COP.
It is an even more preferred embodiment thereof that the refrigerant is or comprises propane (R290). Propane has the advantage to have a relatively low GWP (of 3.3 times the GWP of carbon dioxide), does not destroy the ozone layer, may be used as an alternative to R-12, R-22, R-134a and other chlorinated and/or fluorinated hydrocarbons, and is readily available.
It is an alternative embodiment thereof that the refrigerant is or comprises propylene (R1270).
It is another embodiment that the refrigerant is or comprises HFO-1234yf or 2,3,3,3-Tetra- fluoropropene. HFO-1234yf has almost no environmental impact, acquiring a GWP rating 335 times less than that of the conventional R-134a and an atmospheric lifetime of about 400 times shorter. Furthermore, HFO-1234yf is only mildly flammable. It is a preferred embodiment of the invention that the clothes treatment appliance is a clothes drying appliance, e.g. a stand-alone clothes dryer or a washer-dryer. It is another preferred embodiment of the invention that the clothes treatment appliance is a household appliance.
In the Figures of the attached drawing, the invention is schematically shown by means of an exemplary embodiment, and will be explained further subsequently with reference to that exemplary embodiment. In particular,
Fig.1 shows a schematic drawing of a household tumble dryer using a heat pump; Fig.2 shows a schematic drawing of a heat pump of the tumble dryer; and
Fig.3 shows a sectional side view of a liquid-suction heat interchanger of the heat pump. Fig.1 shows a clothes 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 to be processed clothes. 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. At the evaporator 4 the air A is cooled down and condenses. The resultant condensate is collected in a water tank W. At the evaporator 4, 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. Further downstream the air circuit 6 the now dry and cool air A passes through the condenser 2 where a heat transfer from the condenser 2 and the refrigerant R within 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 working of such a tumble dryer H with its heat pump P (comprising the refrigerant circuit 1 to 5) and its air circuit 6 is well known and does not need to be explained in greater detail.
Fig.2 shows a schematic drawing of a heat pump P'. The heat pump P' may be used in the tumble dryer H instead of the heat pump P. The heat pump P' differs from heat pump P in that it comprises a liquid-suction heat interchanger 8.
As shown in Fig.3, the heat interchanger 8 is of a double pipe design and comprises a first refrigerant line 9 in form of a tubular (suction) pipe 9 having a suction pipe inlet 9i for inputting low pressure refrigerant R and a suction pipe outlet 9o for outputting the vaporous refrigerant R. Centrically through the tubular suction pipe 9 leads a second refrigerant line 10 in form of a tubular (liquid) pipe 10 having a liquid pipe inlet 10i for inputting high pressure refrigerant R and a liquid pipe outlet 10o for outputting the liquid refrigerant R at a respective end. The suction pipe 9 and the liquid pipe 10 are highly thermally con- nected, e.g. by a common metal wall. However, the pipes 9 and 10 are thermally isolated against their environment, to avoid any undue influence of environmental conditions, particular variable environmental temperatures, unto the heat pump. The suction pipe 9 may be thermally less isolated against its environment than the liquid pipe 10. Back to Fig.2, the suction pipe inlet 9i is coupled to an outlet 4o of the evaporator 4 via a refrigerant pipe 5, and the suction pipe outlet 9o is coupled to an inlet 1 i of the compressor 1 via another refrigerant pipe 5. The liquid pipe inlet 10i of the liquid pipe 10 is coupled to an outlet 2o of the condenser 2 and the liquid pipe outlet 10o is coupled to an inlet 3i of the restrictor 3. This kind of connection allows the heat interchanger 8 to cool down refrig- erant R from the condenser outlet 2o (giving a stronger subcooling) and to heat up the evaporator outlet 4o (giving a stronger superheating).
The compressor 1 of the heat pump P' exhibits a displacement lower than 10.5 cc/rev. The outer diameter of the tube or pipe of the tube-and-fins type condenser 2 is 5 mm. The outer diameter of the tube or pipe of the evaporator 4 may also be 5 mm.
The refrigerant R is or comprises propane, propylene and/or HFO-1234yf.
Of course, the invention is not restricted to the embodiments shown.
List of Reference Numerals
1 compressor
1 i inlet of the compressor
2 condenser
2o outlet of the condenser
3 restrictor
3i inlet of the restrictor
4 evaporator
4o evaporator outlet
5 refrigerant line or pipe
6 air circuit
7 rotatable drum
8 liquid-suction heat interchanger
9 suction line or pipe
9i suction pipe inlet
9o suction pipe outlet
10 liquid line or pipe
10i liquid pipe inlet
10o liquid pipe outlet
A process air
H household tumble dryer
P heat pump
P' heat pump
R refrigerant
W water tank

Claims

Claims
Heat pump (Ρ') for a clothes treatment appliance (H),
comprising a compressor (1 ), a condenser (2), a restrictor (3), and an evaporator (4), and further comprising a liquid-suction heat interchanger (8), wherein
the liquid-suction heat interchanger (8) comprises a first refrigerant line (9) and a second refrigerant line (10) that are thermally coupled to each other;
an inlet (9i) of the first refrigerant line (9) of the heat interchanger (8) is coupled to an outlet (4o) of the evaporator (4) and an outlet (9o) of the first refrigerant line (9) is coupled to an inlet (1 i) of the compressor (1 ); and
an inlet (10i) of the second refrigerant line (10) is coupled to an outlet (2o) of the condenser (2) and an outlet (10o) of the second refrigerant line (10) is coupled to an inlet (3i) of the restrictor (3), characterized in that
the first refrigerant line (9) and the second refrigerant line (10) are thermally isolated against an environment of the liquid-suction heat interchanger (8).
Heat pump (Ρ') according to claim 1 , wherein the first refrigerant line (9) is thermally less isolated against the environment of the heat interchanger (8) than the second refrigerant line (10).
Heat pump (Ρ') according to any of the preceding claims, wherein the compressor (1 ) exhibits a displacement of 10.5 cc/rev or less.
Heat pump (Ρ') according to any of the preceding claims, wherein an outer diameter of at least one pipe of the condenser (2) and/or an outer diameter of at least one pipe of the evaporator (4) is less than 7 mm.
Heat pump (Ρ') according to claim 5, wherein an outer diameter of at least one pipe of the condenser (2) and/or an outer diameter at least one pipe of the evaporator (4) is about 5 mm or less. Heat pump (Ρ') according to any of the preceding claims, wherein a refrigerant (R) of the heat pump (Ρ') is a flammable refrigerant (R).
Heat pump (Ρ') according to claim 6, wherein the refrigerant (R) comprises propane or propylene.
Heat pump (Ρ') according to any of claims 6 and 7, wherein the refrigerant (R) comprises HFO-1234yf.
Clothes treatment appliance (H) comprising a heat pump (Ρ'), the heat pump (Ρ') comprising:
a compressor (1 ), a condenser (2), a restrictor (3), and an evaporator (4), and further comprising a liquid-suction heat interchanger (8), wherein
the liquid-suction heat interchanger (8) comprises a first refrigerant line (9) and a second refrigerant line (10) that are thermally coupled to each other;
an inlet (9i) of the first refrigerant line (9) of the heat interchanger (8) is coupled to an outlet (4o) of the evaporator (4) and an outlet (9o) of the first refrigerant line (9) is coupled to an inlet (1 i) of the compressor (1 ); and
an inlet (10i) of the second refrigerant line (10) is coupled to an outlet (2o) of the condenser (2) and an outlet (10o) of the second refrigerant line (10) is coupled to an inlet (3i) of the restrictor (3), characterized in that
the first refrigerant line (9) and the second refrigerant line (10) are thermally isolated against an environment of the liquid-suction heat interchanger (8).
Clothes treatment appliance (H) according to claim 9, wherein the clothes treatment appliance (H) is a clothes drying appliance.
EP13720601.7A 2012-03-30 2013-03-20 Heat pump for a clothes treatment appliance, and clothes treatment appliance comprising such heat pump Active EP2831330B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP13720601.7A EP2831330B1 (en) 2012-03-30 2013-03-20 Heat pump for a clothes treatment appliance, and clothes treatment appliance comprising such heat pump

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP12382127.4A EP2644768A1 (en) 2012-03-30 2012-03-30 Heat pump for a clothes treatment appliance
ES201230640 2012-04-27
EP13720601.7A EP2831330B1 (en) 2012-03-30 2013-03-20 Heat pump for a clothes treatment appliance, and clothes treatment appliance comprising such heat pump
PCT/IB2013/052198 WO2013144780A1 (en) 2012-03-30 2013-03-20 Heat pump for a clothes treatment appliance, and clothes treatment appliance comprising such heat pump

Publications (2)

Publication Number Publication Date
EP2831330A1 true EP2831330A1 (en) 2015-02-04
EP2831330B1 EP2831330B1 (en) 2016-03-16

Family

ID=48289565

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13720601.7A Active EP2831330B1 (en) 2012-03-30 2013-03-20 Heat pump for a clothes treatment appliance, and clothes treatment appliance comprising such heat pump

Country Status (4)

Country Link
EP (1) EP2831330B1 (en)
CN (1) CN104204335B (en)
PL (1) PL2831330T3 (en)
WO (1) WO2013144780A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2871432A1 (en) * 2013-11-06 2015-05-13 BSH Hausgeräte GmbH Heat pump for a household appliance
WO2015172839A1 (en) * 2014-05-16 2015-11-19 Electrolux Appliances Aktiebolag Heat pump laundry dryer
WO2015172840A1 (en) * 2014-05-16 2015-11-19 Electrolux Appliances Aktiebolag Heat pump laundry dryer
CN204394742U (en) * 2014-12-29 2015-06-17 东莞颠覆产品设计有限公司 A kind of real core Nerve Scaffold of built-in degradable metal silk
EP3617392B1 (en) * 2018-08-30 2022-05-25 Electrolux Appliances Aktiebolag Laundry dryer including a heat pump system
DE112019007352B4 (en) 2019-05-23 2024-12-05 Mitsubishi Electric Corporation refrigeration cycle device, refrigeration cycle control system and refrigeration cycle control method

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4286712B2 (en) 2004-05-06 2009-07-01 パナソニック株式会社 Clothes dryer
KR101265605B1 (en) 2006-07-04 2013-05-22 엘지전자 주식회사 laundry treating apparatus
DE102006061737B3 (en) * 2006-12-28 2008-04-24 BSH Bosch und Siemens Hausgeräte GmbH Condensing dryer has fan driven circuit for processing air and a heat pump circuit with a secondary fluid circuit between them
EP2058427A1 (en) * 2007-11-06 2009-05-13 BSH Electrodomésticos España, S.A. Household appliance having a heat pump unit and means for cooling a component thereof
CN201202044Y (en) * 2008-05-06 2009-03-04 上海理工大学 A heat pump dryer
DE102008043920A1 (en) * 2008-11-20 2010-05-27 BSH Bosch und Siemens Hausgeräte GmbH Condensation dryer with a heat pump and method for its operation
ATE540154T1 (en) * 2008-11-21 2012-01-15 Electrolux Home Prod Corp WASHER AND DRYER
EP2261416B1 (en) 2009-06-09 2013-02-20 Electrolux Home Products Corporation N.V. Heat exchanger for a dryer, especially for a domestic dryer
EP2341180A1 (en) * 2009-12-29 2011-07-06 Electrolux Home Products Corporation N.V. A heat pump system for a tumble dryer
EP2385169A1 (en) * 2010-05-03 2011-11-09 Electrolux Home Products Corporation N.V. A laundry machine with heat pump system and a method for operating the laundry machine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2013144780A1 *

Also Published As

Publication number Publication date
EP2831330B1 (en) 2016-03-16
PL2831330T3 (en) 2016-09-30
CN104204335A (en) 2014-12-10
WO2013144780A1 (en) 2013-10-03
CN104204335B (en) 2016-10-26

Similar Documents

Publication Publication Date Title
EP2831330B1 (en) Heat pump for a clothes treatment appliance, and clothes treatment appliance comprising such heat pump
US20140109428A1 (en) Dryer
CN201245785Y (en) Household electrical appliance with heat pump
JP5409715B2 (en) Air conditioner
US9146056B2 (en) Laundry treating apparatus having expansion valve which is variable according to the driving mode
EA016181B1 (en) Household appliance containing a heat transfer fluid
EA014949B1 (en) Condensation dryer having a heat pump and method for the operation thereof
CN102656314B (en) Comprise the household electrical appliance of expansion system
EP2385169A1 (en) A laundry machine with heat pump system and a method for operating the laundry machine
US20140041400A1 (en) Heat pump system for a laundry dryer and a method for operating a heat pump laundry dryer
Mancini et al. Thermodynamic analysis and experimental investigation of a CO2 household heat pump dryer
EP2468948B1 (en) Dehumidifying and heating apparatus and clothes drying machine using the same
EP2735819B1 (en) Refrigeration cycle apparatus and warm water producing apparatus having refrigeration cycle apparatus
Gatarić et al. Evaluating R450A as a drop-in replacement for R134a in household heat pump tumble dryers
JP5625883B2 (en) Dehumidifying and heating device and clothes dryer provided with the same
CN105705899A (en) Heat pump for a household appliance
WO2011080116A1 (en) Heat pump laundry dryer
TW200426332A (en) Cooling apparatus
EP2644768A1 (en) Heat pump for a clothes treatment appliance
JP2016123770A (en) Washing and drying machine
EP2871432A1 (en) Heat pump for a household appliance
JP5617602B2 (en) Dehumidifying and heating device and clothes dryer provided with the same
JP6675083B2 (en) Binary heat pump device
CN105121730A (en) Appliance for drying laundry
EP2639538A1 (en) Heat-exchanger cover

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20141030

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

AX Request for extension of the european patent

Extension state: BA ME

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: BSH HAUSGERAETE GMBH

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20151103

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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: AT

Ref legal event code: REF

Ref document number: 781364

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160415

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602013005559

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20160316

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

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: 20160316

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: 20160616

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: 20160316

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: 20160617

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 781364

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160316

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

Ref country code: LT

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

Effective date: 20160316

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: 20160316

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: 20160316

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: 20160316

Ref country code: BE

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

Effective date: 20160331

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: 20160316

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

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: 20160716

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: 20160316

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: 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: 20160316

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: 20160316

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: 20160718

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: 20160316

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: 20160316

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: 20160316

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: 20160316

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602013005559

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160316

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: 20160316

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

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

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

Ref country code: 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: 20160316

Ref country code: LI

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

Effective date: 20160331

Ref country code: CH

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

Effective date: 20160331

Ref country code: IE

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

Effective date: 20160320

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20170111

26N No opposition filed

Effective date: 20161219

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: 20160616

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: 20160517

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

Ref country code: SI

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

Effective date: 20160316

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

Ref country code: MT

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

Effective date: 20160316

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

Ref country code: HU

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

Effective date: 20130320

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

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: 20160316

Ref country code: MT

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

Effective date: 20160331

Ref country code: CY

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

Effective date: 20160316

Ref country code: MK

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

Effective date: 20160316

Ref country code: LU

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

Effective date: 20160320

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

Ref country code: AL

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

Effective date: 20160316

Ref country code: TR

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

Effective date: 20160316

REG Reference to a national code

Ref country code: DE

Ref legal event code: R084

Ref document number: 602013005559

Country of ref document: DE

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

Ref country code: PL

Payment date: 20230310

Year of fee payment: 11

Ref country code: GB

Payment date: 20230323

Year of fee payment: 11

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20240320

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

Ref country code: GB

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

Effective date: 20240320

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

Ref country code: GB

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

Effective date: 20240320

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

Ref country code: PL

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

Effective date: 20240320

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

Ref country code: DE

Payment date: 20260331

Year of fee payment: 14