EP2549007A1 - Heat pump laundry treatment apparatus - Google Patents
Heat pump laundry treatment apparatus Download PDFInfo
- Publication number
- EP2549007A1 EP2549007A1 EP11174963A EP11174963A EP2549007A1 EP 2549007 A1 EP2549007 A1 EP 2549007A1 EP 11174963 A EP11174963 A EP 11174963A EP 11174963 A EP11174963 A EP 11174963A EP 2549007 A1 EP2549007 A1 EP 2549007A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat exchanger
- blower
- cooling air
- compressor
- refrigerant
- 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
Links
- 239000003570 air Substances 0.000 claims abstract description 175
- 238000001816 cooling Methods 0.000 claims abstract description 126
- 239000003507 refrigerant Substances 0.000 claims abstract description 64
- 238000000034 method Methods 0.000 claims abstract description 46
- 238000012545 processing Methods 0.000 claims abstract description 16
- 239000012080 ambient air Substances 0.000 claims abstract description 12
- 238000010438 heat treatment Methods 0.000 claims abstract description 12
- 238000005406 washing Methods 0.000 claims abstract description 6
- 238000007664 blowing Methods 0.000 claims abstract description 5
- 238000001035 drying Methods 0.000 claims abstract description 3
- 238000005192 partition Methods 0.000 claims description 4
- UQMRAFJOBWOFNS-UHFFFAOYSA-N butyl 2-(2,4-dichlorophenoxy)acetate Chemical compound CCCCOC(=O)COC1=CC=C(Cl)C=C1Cl UQMRAFJOBWOFNS-UHFFFAOYSA-N 0.000 description 12
- 241000237983 Trochidae Species 0.000 description 3
- 238000009413 insulation Methods 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 239000004753 textile Substances 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000005465 channeling Effects 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000000151 deposition Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 210000002683 foot Anatomy 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
Images
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 laundry treatment apparatus having a heat pump system, in particular a dryer, a washing machine or a washer-dryer.
- DE 44 09 607 A1 suggests a laundry dryer using a heat pump system with a closed process air loop and a refrigerant loop.
- a compressor drives the refrigerant through a condenser, an expansion valve, an evaporator and back to the inlet of the compressor.
- radiator rips are arranged at the refrigerant pipe. Cooling air is blown by a blower to the radiator rips for cooling the refrigerant and removing excess heat from the heat pump system.
- a laundry treatment apparatus in which the laundry to be treated can be stored in a laundry storing chamber, which is preferably a rotatably supported drum.
- the laundry is treated by process air, which is preferably completely or at least for the most part of it circulated in a closed processing air loop.
- the process air loop is formed by the process air flow through the laundry storing chamber and a process air channel that guides the air from the outlet to the inlet of the storing chamber.
- the process air is conveyed by a process air blower, which for example in the embodiment of the rotatable drum can be driven by a motor for driving the drum.
- the laundry treatment apparatus has a heat pump system for dehumidifying and heating the process air.
- Dehumidifying is made by cooling the process air at a first heat exchanger of the heat pump system (e.g. an evaporator or refrigerant gas heater). Heating is made at a second heat exchanger of the laundry treatment apparatus (e.g. a condenser or refrigerant gas cooler).
- First and second heat exchangers are serially connected in a refrigerant loop in which the refrigerant is driven by a compressor and expanded by a refrigerant expansion device.
- auxiliary heat exchanger e.g. auxiliary condenser or gas cooler.
- the auxiliary heat exchanger is connected in the refrigerant loop serially upstream (with respect to the refrigerant flow) or downstream or partially upstream and partially downstream the second heat exchanger. Or the auxiliary heat exchanger is connected in parallel to the second heat exchanger.
- the auxiliary heat exchanger is adapted to transfer heat from the refrigerant to cooling and/or ambient air ('cooling air' in the following). Additionally depositing the heat in liquid may be provided, for example in water stored in the apparatus (e.g. washing water when the apparatus is a washer-dryer).
- a cooling air blower is assigned to the auxiliary heat exchanger for blowing or sucking cooling air through the auxiliary heat exchanger.
- a shielding device is arranged such that the compressor is shielded against the cooling air blown by the blower and/or the compressor is shielded by providing an compressor insulation adapted to prevent heat exchange between the compressor and the compressor's outer ambient. With the insulation heat exchange between the compressor and the air surrounding the compressor and the cooling air moved by the cooling air blower is prevented or essentially prevented.
- the operation temperature of the compressor is independent from the influence by the cooling air.
- the compressor's ambient or outer wall temperature is independent from the cooling air being driven by the cooling air blower or not, the cooling air temperature, the spatial cooling effect on the compressor's outer case and/or the cooling air flow rate.
- the operation temperature of the compressor is independent of the cooling air characteristics and variations which results in an improved uniformity of the compressor operation temperature over time is achieved. This in turn improves its operation efficiency and long-life cycle.
- the excessive heat amount is removed from the refrigerant without increasing the compressor heat losses. Therefore the temperature level of the refrigerant and of the process air is kept quite constant while the temperature of the compressor is kept under safety level without penalizing the performances of the system.
- the maximum cooling capacity of the combination auxiliary heat exchanger and cooling air flow rate driven by the blower is in the range of the heating capacity (heat power) deposited by the compressor in the heat pump system.
- the heating power i.e. at the second heat exchanger
- the cooling power i.e. at the first heat exchanger
- P(second heat exchanger) P(first heat exchanger)+ P(power compressor) - P(power loss) where power loss is the amount of power lost and transferred to the environment.
- the cooling capacity of the auxiliary heat exchanger is in the range of 10 to 100%, 15 to 80%, 20 to 60% of the P(power compressor).
- the shielding device is arranged between the compressor and the auxiliary heat exchanger and/or the cooling air blower.
- the blower may be arranged between the shielding device and the auxiliary heat exchanger or the auxiliary heat exchanger is arranged between the shielding device and the blower.
- the blower blows or sucks the cooling air through the auxiliary heat exchanger.
- the shielding device may be formed by, may be partially formed by or is a partition wall, a component housing and/or a process air duct section.
- a section of the process air duct is arranged between blower and auxiliary heat exchanger on the one side and the compressor on the other side of the duct section.
- a drive motor housing and/or a power electronics housing is arranged to shield the compressor.
- a separate partition wall is provided to shield the compressor.
- the shielding device may be formed at a bottom shell of the apparatus, preferably as an integral or monolithic part therewith (e.g.
- the shielding device additionally has a guiding function for guiding the cooling air from or to a housing opening to exhaust or inhale the cooling air at a predetermined opening in the apparatus housing, in particular a predetermined opening at the bottom wall, a side wall and/or a bottom shell of the apparatus cabinet.
- the air flow guiding or deflection function of the shielding device is used for example to deflect the air flow direction with respect to the cooling air flow direction which is given by the geometry of the cooling air blower and/or the auxiliary heat exchanger.
- the shielding device having deflection function gives more freedom in the design and integration of the auxiliary heat exchanger/cooling air blower in the spatial layout of the apparatus.
- the shielding device In addition to shield the cooling air flow in a potential path to the compressor, it is advantageous to provide the shielding device with one or more side shields each at a respective side of the auxiliary heat exchanger (i.e. on one or more sides thereof).
- the side shield(s) extend partially or fully along a lateral side of the auxiliary heat exchanger and provide(s) additional channeling of the cooling air flow to improve efficiency in cooling of the auxiliary heat exchanger and shielding the compressor.
- At least a portion of the cooling air flow is guided to another component of the apparatus, for example to power electronics of the apparatus, like a power converter for the compressor and/or the drum driving motor, and/or to a motor of the apparatus, like the drum drive motor.
- power electronics of the apparatus like a power converter for the compressor and/or the drum driving motor
- a motor of the apparatus like the drum drive motor.
- an auxiliary or branching cooling air guiding channel is used to guide the airflow to such other component(s).
- the auxiliary or branching cooling air channel has an input or an outlet at the shielding surface of the shielding device.
- the main components of the heat pump system are arranged in a base section of the apparatus and a section of a process air channel is arranged in a middle region of the base section.
- this section of the process air channel houses the first and second heat exchanger, wherein this arrangement is sometimes called the 'battery' of the heat pump system.
- the compressor is arranged at one side of the middle process air channel section and the auxiliary heat exchanger and the cooling air blower are arranged at another side of the middle channel section opposite to the compressor. In this way the middle channel section forms the shielding device shielding cooling air from being blown towards or being sucked from the compressor.
- the cooling air blower and the auxiliary heat exchanger are arranged at a height level above the first and second heat exchanger, for example above the battery or the cooling air channel in which the first and second heat exchanger are arranged.
- the cooling air flow path is offset to the compressor location and cooling of the compressor is prevented.
- the auxiliary heat exchanger has a cooling power in the range from 10 to 500 W, 50 to 450 W or 100 to 450 W, and/or the auxiliary heat exchanger is adapted to reduce the refrigerant temperature by 2 to 18°C, 5 to 15°C, 8 to 13°C or 10 to 15°C.
- the maximum conveyance capacity of the cooling air blower is in the range of 10 to 180 m 3 /h, 20 to 100 m 3 /h, or 40 to 80 m 3 /h.
- the operation of the laundry treatment apparatus is controlled by control unit, including the operation and monitoring of the heat pump system.
- control unit is adapted to activate the cooling air blower after the warm-up phase or when approaching the steady state. End of the warm-up phase or arriving or approaching the steady state is for example detected by a sensor device detecting the temperature and/or pressure of the refrigerant (or being dependent on the refrigerant) at a predefined location of the refrigerant loop, for example at or close to the first heat exchanger inlet or outlet.
- the control unit is adapted to keep the blower operating during the steady state until the running laundry treatment process is finished.
- the conveyance or flow rate or rotation speed of the cooling air blower may be varied around a non-zero value without undershooting the zero value so as to keep continuous (positive) operation of the blower.
- Variation of the conveyance rate of the blower may be required to keep the operation condition of the heat pump system at a predetermined level or within a predetermined target range for optimizing the heat pump system efficiency and/or maintaining the steady state.
- Adaptation of cooling air flow rate may be required during a treatment cycle, if for example the laundry is to be dried and laundry humidity decreases, or if the cooling air is ambient air having a varying ambient air temperature.
- Fig. 1 depicts in a schematic representation a home appliance 2 which in this embodiment is a heat pump tumble dryer.
- the tumble dryer comprises a heat pump system 4, including in a closed refrigerant loop in this order of refrigerant flow B: a first heat exchanger 10 acting as evaporator (gas heater) for evaporating (heating) the refrigerant and cooling process air, a compressor 14, a second heat exchanger 12 acting as condenser (gas cooler) for cooling the refrigerant and heating the process air, an auxiliary heat exchanger 34 acting as additional condenser, and an expansion device 16 from where the refrigerant is returned to the first heat exchanger 10.
- a first heat exchanger 10 acting as evaporator (gas heater) for evaporating (heating) the refrigerant and cooling process air
- a compressor 14 a second heat exchanger 12 acting as condenser (gas cooler) for cooling the refrigerant and heating the process air
- an auxiliary heat exchanger 34 acting as additional condens
- the heat pump system forms a refrigerant loop 6 through which - in normal operation - the refrigerant is circulated by the compressor 14 as indicated by arrow B.
- the auxiliary condenser 34 dissipates heat to the ambient of the dryer 2 in the steady state of the heat pump system 4 in which maximum or nearly maximum operation condition is achieved after the warm-up period and the heat deposited by the compressor in the refrigerant loop 6 has to be removed via auxiliary condenser 34 to prevent overheating.
- the sequence of the components in the refrigerant loop can be modified in the embodiments herein in that the auxiliary condenser 34 is not placed between the condenser 12 and the expansion device 16 with respect to refrigerant flow, but between the compressor 14 and the condenser 12 (not shown). This modification is applicable to all embodiments herein.
- the expansion device 16 is a controllable valve that operates under the control of a control unit to adapt the flow resistance for the refrigerant in dependency of operating states of the heat pump system.
- the expansion device 16 can be a capillary tube, a valve with fixed expansion cross-section, a throttle valve with variable cross section that automatically adapts the expansion cross-section in dependency of the refrigerant pressure (e.g. by elastic or spring biasing), a semi-automatic throttle valve in which the expansion cross-section is adapted in dependency of the temperature of the refrigerant (e.g. by actuation of a thermostat and/or where the temperature of the refrigerant is taken between the gas cooler and the gas heater, the gas heater and the compressor, or the compressor and the gas cooler), or the like.
- the process air flow within the home appliance 2 is guided through a compartment 18 of the home appliance 2, i.e. through a compartment 18 for receiving articles to be treated, e.g. a drum 18.
- the articles to be treated are textiles, laundry 19, clothes, shoes or the like. In the embodiments here these are preferably textiles, laundry or clothes.
- the process air flow is indicated by arrows A in Fig. 1 and is driven by a process air blower 8. Outside the drum 18 the process air A is guided through an air channel 20.
- the air exiting the drum 18 through the drum outlet (which is the loading opening of the drum) is filtered by a first fluff filter 22 arranged close to the drum outlet in or at the channel 20.
- the first heat exchanger 10 transfers heat from the process air to the refrigerant.
- humidity from the process air condenses at the first heat exchanger 10 is collected there and the collected condensate is drained to a condensate collector 30.
- the process air cooled and dehumidified when passing the first heat exchanger passes then through the second heat exchanger 12 where heat is transferred from the refrigerant to the process air.
- the process air is sucked from exchanger 12 by the blower 8 and driven into the drum 18 where it heats up the laundry 19 and receives the humidity therefrom.
- the main components of the heat pump system 4 are arranged in a base section 5 or basement of the dryer 2, different embodiments of which are shown in the following figures.
- the process air channel 20 guides the process air flow A outside the drum 18 and includes different sections, including the section forming the battery channel 20a in which the first and second heat exchangers 10, 12 are arranged.
- the process air exiting the second heat exchanger 12 flows into a rear channel 20b in which the process air blower 8 is arranged.
- the air conveyed by blower 8 is guided upward in a rising channel 20c to the backside of the drum 18.
- E shows the respective time behavior for the dryer 2 according to the invention in which the heat pump system 4 is cooled using only or essentially the auxiliary condenser 34 for removing the excessive heat during the steady state after the warm-up period.
- a cooling air blower 28 is activated and continuously operated during the steady phase without cooling down the compressor 14.
- the heat loss factor is the percentage of the power adsorbed by the compressor that is lost as heat losses.
- the lower this value the better for the system efficiency. From Fig. 12 it is clear that continuous operation of the blower 28 and keeping the compressor at constant temperature is advantageous over the operation mode in prior art heat pump systems.
- the cooling air blower 28 when reaching or approaching the steady state the cooling air blower 28 is activated and continuously operated.
- the cooling capacity of the auxiliary condenser 34 is fully used (as compared to the conventional intermittent operation) and the cooling capacity of the auxiliary condenser 34 can be reduced.
- Fig. 2 shows a top view of the heat pump system 4 of the dryer 2 arranged in the dryer base section 5.
- the base section is housing the heat pump system and parts of the process air channel 20 in a bottom shell 40 forming the base frame of the dryer and having the dryer foots (compare Fig. 6 ).
- a cover shell 42 is placed over the bottom shell 40, wherein portions of both shells form the battery channel 20a in which the first and second heat exchanger 10, 12 (which form the battery of the heat pump system) are encased.
- the rear channel 20b and the blower 8 are also encased by bottom and top shell 40, 42.
- the reference numerals partially (e.g.
- blower 8 and the drum 18 have been placed at or over section of the top shell 42 where the component covered by the top shell actually can not be seen, but its location is indicated thereby.
- the motor 9 for driving blower 8 and the drum 18 is also located under the cover shell 42 and in this embodiment is located between blower 8 and compressor 14.
- the second fluff filter 24 is placed in a drawer inserted into the lower part of the process air channel 20.
- the condensate water that is condensing at the first heat exchanger 10 is collected in a tray formed below the exchanger 10 in the bottom shell 40 and is guided in a condensate channel at the side of the second heat exchanger 12 into the condensate collector 30 formed by a rear section of the bottom shell 40.
- a level sensor and a condensate pump are arranged at the collector 30 to pump the condensate to a condensate reservoir at the top of the dryer.
- the auxiliary condenser 34 is placed in an upright orientation in the bottom shell 40 such that its slender top side is seen in Fig. 2 .
- the cooling air blower 28 is arranged which sucks in ambient air through openings in the bottom shell 40 at the basement front side of the dryer 2.
- the conveyed cooling air passes through the condenser 34 from the lower side as shown in Fig. 2 and exits at the upper side the condenser 34 which is the rear side of the condenser when seen from front of the dryer.
- the cooling air exiting the condenser 34 is guided downward by a deflector shield 36 placed immediately behind the condenser, facing its rear or exit side.
- Fig. 3 shows in cross-section an enlarged section of the lower right side of Fig. 2 where the auxiliary condenser 34 is placed.
- the radiator rips of condenser 34 can be seen arranged around the zigzag or meander-shaped refrigerant pipe.
- Shield 36 has a side shield 37 that is running at both lateral sides partially over the depth of condenser 34 (the depth direction is the cooling air passing direction) and completely over the top side of the condenser.
- the partial side shield portions 37 can be seen in cross section in Fig.
- the shield is enclosing the rear side, partial lateral side and top side of condenser 34 and is open towards the front side (condenser air inlet) and bottom side (air outlet).
- Fig. 4 is a lateral cross section of a part of the base section 5 in the region of the condenser 34 along a cross section line from the front of the dryer (left side in Fig. 4 ) towards the rear side of the dryer.
- Dashed arrow C indicates the cooling or ambient air flow conveyed by blower 28 through the auxiliary condenser 34 and deflected at its backside downward by the deflector shield 36.
- the air flow C exits the base section 5 through openings 38 formed in the bottom shell 40.
- the openings 38 can be seen in more detail in the view from below in Fig. 6 .
- Fig. 5 shows a perspective view to the base section 5 with the cover shell 42, second fluff filter 24 (drawer), blower 8 and motor 9 removed.
- Fig. 7 the lateral side view of the base section 5 is shown completely as compared to Fig. 4 .
- the cover shell 42 is placed in position and over the motor 9 section of cover shell 42 the power converter 44 for the compressor 14 (and/or other power electronics) is mounted.
- a branching channel 46 is provided as schematically shown in Fig. 7 .
- the branching channel 46 has a cooling air inlet at the deflector shield 36 and an outlet to the housing encasing the power electronics 44. As soon as the blower 28 is activated, a portion of the ambient air that passed the auxiliary condenser 34 is guided to the power electronics 4 for cooling it.
- Figs. 8 to 11 show as schematic view the arrangement of heat pump components in the base section 5 in top view according to other embodiments.
- the same reference numerals for components of the heat pump system 4 operating the same way as the components in Figs. 1 to 7 are used. For simplicity reference is made to the above and deviating implementations are indicated below.
- the blower 8, drum and blower motor 9 and compressor 14 are arranged on a first side of the battery channel 20a, and the blower 28, the condenser 34 and the power electronics 44 are arranged on a second side of the battery channel 20a.
- the battery channel 20a is forming a center or middle section of the base section 5 running from a front region to the back region of the base section 5. It provides a partition wall or deflector shield 36a preventing a cooling or ambient air flow from the cooling air blower 28 to the compressor 14.
- the power electronics 44 is not arranged in the flow path of the cooling air.
- the power electronics is arranged above the motor 9 similarly as shown in Fig. 7 .
- the cooling air flow C is sucked in by blower 28 through openings in the front region of the base section 5, is pushed by the blower 28 through the condenser 34 towards power electronics 44, is deflected by the outer case of the condensate collector to the side and exits the base section 5 through openings at a side wall thereof.
- the cooling air flow C is reversed and/or the blower 28 is arranged on the rear side of condenser 34 (when seen from the front of dryer 2).
- the depth of the dryer may be decreased as compared to the 60 cm depth of a conventional dryer.
- the depth of such dryer type is maximum or less than 55 cm, 50 cm or 45 cm.
- the volume of the drum is reduced at the same time while the drum diameter is full size adapted to the 60 cm width of conventional dryers.
- With reduced drum volume the required drying capacity is reduced and the dimension or capacity of the components of the heat pump system 4 can be reduced.
- narrowing the battery channel 20a width as indicated in Fig. 8 is easily implemented.
- Such dryer is adapted for small apartment use or single/double household needs.
- the battery channel 20a is arranged on the left side of the base section 5.
- a deflector shield 36b is arranged between the compressor 14 at one side and the condenser 34 and blower 28 at the other side to prevent cooling air flow to the compressor.
- the blower 28 sucks the cooling air flow C through openings on the left side of the base section and through the auxiliary condenser 34 and blows it against the power electronics 44 and the motor 9.
- Exhaust of the air flow C is through openings on the lateral side and/or in the bottom of base section 5 (bottom shell 40).
- the flow direction of air flow C is reversed and/or the power electronics and/or the motor 9 are not in the cooling air flow path.
- the housing of motor 9 is arranged between the cooling air flow C and the compressor 14 thus forming a deflector shield 36c.
- the blower 28 sucks the cooling air through openings in the bottom shell 40 and pushes it through the auxiliary condenser 34 against shield 36c which deflects the flow C through openings in the lateral side of base section 5.
- auxiliary condenser 34, blower 28 and power electronics 44 are placed on top and/or above the battery channel 20a (containing evaporator 10 and condenser 12).
- the power electronics 44 is not in the flow path of cooling air C and instead e.g. placed on the case of motor 9 (compare Fig. 7 ).
- a deflector shield 36d in the form of a cooling air channel wall is provided to guide the air flow C and prevent flowing it towards compressor 14.
- the cooling air channel 36d covers the lateral side and the top side of the components 34, 28 and 44.
- the flow direction of air flow C is inverted and/or the channel 36d has openings not at the lateral side wall of the base section, but on the front side of the base section 5.
- the cooling air channel 36d preferably is arranged on the outermost left side above the upper level of the battery channel 20a and is preferably small in width as compared to the battery channel 20a. Thereby the lowest point of the drum 18 can be kept close to the upper side of battery channel 20a, while the dead space at the left side within the dryer body is used to arrange the cooling air channel.
- the cooling air channel is arranged at the outermost right side above the level of the battery channel 20a and/or the case of the motor 9. Compare the position of the power electronics 44 in Fig. 7 - such that the channel 36d takes the position of electronics 44 and preferably does not extend the complete depth of the base section 5, e.g. by providing cooling air inlet or outlet openings at a lateral side or bottom side of the vertically extended base section 5.
- cooling air blower 28 is depicted and arranged as axial blower (axial fan in which the air flow C enters and exits in the axial direction with respect to the blower rotation axis).
- axial blower axial fan in which the air flow C enters and exits in the axial direction with respect to the blower rotation axis.
- a radial blower radial fan or centrifugal fan
- tangential blower cross-flow fan
- the backside wall of the radial blower (which is opposite to the inlet opening for the conveyed air) can at the same time represent the deflector shield (shielding device) that prevents air flow to the compressor 14.
- the cooling air can be sucked through the auxiliary condenser 34 when the radial blower is arranged in the direction of the outlet side of the condenser 34.
- the cooling air conveyed by the radial blower can then be exhausted into a direction perpendicular to the exit air direction (i.e. preferably the axial inlet direction of the radial blower). For example through openings in the bottom of bottom shell 40.
- a direction perpendicular to the exit air direction i.e. preferably the axial inlet direction of the radial blower.
- auxiliary condenser 34 and blower 28 from front to rear can be changed such that the condenser 34 is close to the front opening and the blower is on the backside of condenser 34 and exhausts the cooling air through the outlet openings 38.
- the radial blower with its housing replaces the axial blower 28 and the deflector shield 36.
Landscapes
- Engineering & Computer Science (AREA)
- Textile Engineering (AREA)
- Detail Structures Of Washing Machines And Dryers (AREA)
Abstract
Description
- The invention relates to a laundry treatment apparatus having a heat pump system, in particular a dryer, a washing machine or a washer-dryer.
-
DE 44 09 607 A1 suggests a laundry dryer using a heat pump system with a closed process air loop and a refrigerant loop. In the refrigerant loop a compressor drives the refrigerant through a condenser, an expansion valve, an evaporator and back to the inlet of the compressor. Near the inlet and outlet of the condenser, radiator rips are arranged at the refrigerant pipe. Cooling air is blown by a blower to the radiator rips for cooling the refrigerant and removing excess heat from the heat pump system. - It is an object of the invention to provide a laundry treatment apparatus in which the operation stability and/or efficiency is improved.
- The invention is defined in claim 1. Particular embodiments are set out in the dependent claims.
- According to claim 1, a laundry treatment apparatus is provided in which the laundry to be treated can be stored in a laundry storing chamber, which is preferably a rotatably supported drum. The laundry is treated by process air, which is preferably completely or at least for the most part of it circulated in a closed processing air loop. Preferably the process air loop is formed by the process air flow through the laundry storing chamber and a process air channel that guides the air from the outlet to the inlet of the storing chamber. Preferably the process air is conveyed by a process air blower, which for example in the embodiment of the rotatable drum can be driven by a motor for driving the drum.
- The laundry treatment apparatus has a heat pump system for dehumidifying and heating the process air. Dehumidifying is made by cooling the process air at a first heat exchanger of the heat pump system (e.g. an evaporator or refrigerant gas heater). Heating is made at a second heat exchanger of the laundry treatment apparatus (e.g. a condenser or refrigerant gas cooler). First and second heat exchangers are serially connected in a refrigerant loop in which the refrigerant is driven by a compressor and expanded by a refrigerant expansion device.
- After the warm-up phase of the heat pump system, the excessive heat is removed by an auxiliary heat exchanger (e.g. auxiliary condenser or gas cooler). The auxiliary heat exchanger is connected in the refrigerant loop serially upstream (with respect to the refrigerant flow) or downstream or partially upstream and partially downstream the second heat exchanger. Or the auxiliary heat exchanger is connected in parallel to the second heat exchanger. The auxiliary heat exchanger is adapted to transfer heat from the refrigerant to cooling and/or ambient air ('cooling air' in the following). Additionally depositing the heat in liquid may be provided, for example in water stored in the apparatus (e.g. washing water when the apparatus is a washer-dryer). A cooling air blower is assigned to the auxiliary heat exchanger for blowing or sucking cooling air through the auxiliary heat exchanger.
- According to the invention a shielding device is arranged such that the compressor is shielded against the cooling air blown by the blower and/or the compressor is shielded by providing an compressor insulation adapted to prevent heat exchange between the compressor and the compressor's outer ambient. With the insulation heat exchange between the compressor and the air surrounding the compressor and the cooling air moved by the cooling air blower is prevented or essentially prevented. By thus preventing the compressor's outer surface being cooled by cooling air the operation temperature of the compressor is independent from the influence by the cooling air. For example the compressor's ambient or outer wall temperature is independent from the cooling air being driven by the cooling air blower or not, the cooling air temperature, the spatial cooling effect on the compressor's outer case and/or the cooling air flow rate. Hence the operation temperature of the compressor is independent of the cooling air characteristics and variations which results in an improved uniformity of the compressor operation temperature over time is achieved. This in turn improves its operation efficiency and long-life cycle.
- With the shielding/insulation, the excessive heat amount is removed from the refrigerant without increasing the compressor heat losses. Therefore the temperature level of the refrigerant and of the process air is kept quite constant while the temperature of the compressor is kept under safety level without penalizing the performances of the system.
- Preferably the maximum cooling capacity of the combination auxiliary heat exchanger and cooling air flow rate driven by the blower is in the range of the heating capacity (heat power) deposited by the compressor in the heat pump system. In the heat pump system the heating power (i.e. at the second heat exchanger) is higher than the cooling power (i.e. at the first heat exchanger) according the following: P(second heat exchanger) = P(first heat exchanger)+ P(power compressor) - P(power loss) where power loss is the amount of power lost and transferred to the environment. As in the steady state the net power deposited in and removed from the process air loop is zero, which means P(first heat exchanger) = P(second heat exchanger), the auxiliary heat exchanger needs a cooling capacity of about P(auxiliary heat exchanger) = P(power compressor) - P(power loss). As under normal conditions heat is dissipated from the process air loop and the refrigerant loop through other channels (e.g. heat loss through laundry storing chamber walls), the cooling capacity of the auxiliary heat exchanger (P(auxiliary heat exchanger)) is in the range of 10 to 100%, 15 to 80%, 20 to 60% of the P(power compressor).
- Preferably the shielding device is arranged between the compressor and the auxiliary heat exchanger and/or the cooling air blower. Relating to the cooling air flow path the blower may be arranged between the shielding device and the auxiliary heat exchanger or the auxiliary heat exchanger is arranged between the shielding device and the blower. In embodiments the blower blows or sucks the cooling air through the auxiliary heat exchanger.
- In an embodiment the shielding device may be formed by, may be partially formed by or is a partition wall, a component housing and/or a process air duct section. For example a section of the process air duct is arranged between blower and auxiliary heat exchanger on the one side and the compressor on the other side of the duct section. Or a drive motor housing and/or a power electronics housing is arranged to shield the compressor. Or a separate partition wall is provided to shield the compressor. The shielding device may be formed at a bottom shell of the apparatus, preferably as an integral or monolithic part therewith (e.g. in a mold process with the bottom shell), and/or the shielding device additionally has a guiding function for guiding the cooling air from or to a housing opening to exhaust or inhale the cooling air at a predetermined opening in the apparatus housing, in particular a predetermined opening at the bottom wall, a side wall and/or a bottom shell of the apparatus cabinet. The air flow guiding or deflection function of the shielding device is used for example to deflect the air flow direction with respect to the cooling air flow direction which is given by the geometry of the cooling air blower and/or the auxiliary heat exchanger. The shielding device having deflection function gives more freedom in the design and integration of the auxiliary heat exchanger/cooling air blower in the spatial layout of the apparatus.
- In addition to shield the cooling air flow in a potential path to the compressor, it is advantageous to provide the shielding device with one or more side shields each at a respective side of the auxiliary heat exchanger (i.e. on one or more sides thereof). The side shield(s) extend partially or fully along a lateral side of the auxiliary heat exchanger and provide(s) additional channeling of the cooling air flow to improve efficiency in cooling of the auxiliary heat exchanger and shielding the compressor.
- In a preferred embodiment at least a portion of the cooling air flow is guided to another component of the apparatus, for example to power electronics of the apparatus, like a power converter for the compressor and/or the drum driving motor, and/or to a motor of the apparatus, like the drum drive motor. If only a portion of the cooling air flow is to be used to cool such other components, preferably an auxiliary or branching cooling air guiding channel is used to guide the airflow to such other component(s). In an embodiment the auxiliary or branching cooling air channel has an input or an outlet at the shielding surface of the shielding device.
- Preferably the main components of the heat pump system (at least the first and second heat exchangers and the compressor) are arranged in a base section of the apparatus and a section of a process air channel is arranged in a middle region of the base section. Preferably this section of the process air channel houses the first and second heat exchanger, wherein this arrangement is sometimes called the 'battery' of the heat pump system. In an embodiment the compressor is arranged at one side of the middle process air channel section and the auxiliary heat exchanger and the cooling air blower are arranged at another side of the middle channel section opposite to the compressor. In this way the middle channel section forms the shielding device shielding cooling air from being blown towards or being sucked from the compressor. Alternatively the cooling air blower and the auxiliary heat exchanger are arranged at a height level above the first and second heat exchanger, for example above the battery or the cooling air channel in which the first and second heat exchanger are arranged. In this case again the cooling air flow path is offset to the compressor location and cooling of the compressor is prevented.
- Preferably for achieving the cooling power to remove the excessive heat during the steady state (see above) the auxiliary heat exchanger has a cooling power in the range from 10 to 500 W, 50 to 450 W or 100 to 450 W, and/or the auxiliary heat exchanger is adapted to reduce the refrigerant temperature by 2 to 18°C, 5 to 15°C, 8 to 13°C or 10 to 15°C. Additionally or alternatively the maximum conveyance capacity of the cooling air blower is in the range of 10 to 180 m3/h, 20 to 100 m3/h, or 40 to 80 m3/h.
- In an embodiment the operation of the laundry treatment apparatus is controlled by control unit, including the operation and monitoring of the heat pump system. Preferably the control unit is adapted to activate the cooling air blower after the warm-up phase or when approaching the steady state. End of the warm-up phase or arriving or approaching the steady state is for example detected by a sensor device detecting the temperature and/or pressure of the refrigerant (or being dependent on the refrigerant) at a predefined location of the refrigerant loop, for example at or close to the first heat exchanger inlet or outlet. Preferably the control unit is adapted to keep the blower operating during the steady state until the running laundry treatment process is finished.
- In an embodiment the conveyance or flow rate or rotation speed of the cooling air blower may be varied around a non-zero value without undershooting the zero value so as to keep continuous (positive) operation of the blower. Variation of the conveyance rate of the blower may be required to keep the operation condition of the heat pump system at a predetermined level or within a predetermined target range for optimizing the heat pump system efficiency and/or maintaining the steady state. Adaptation of cooling air flow rate may be required during a treatment cycle, if for example the laundry is to be dried and laundry humidity decreases, or if the cooling air is ambient air having a varying ambient air temperature. Then the control unit can adapt the cooling air flow rate to keep the cooling capacity of the auxiliary heat exchanger at or approximately at the excess heat power deposited by the compressor in the system, i.e. P(auxiliary heat exchanger) = P(power compressor) - P(power loss), within the ranges indicated above.
- Reference is made in detail to preferred embodiments of the invention, examples of which are illustrated in the accompanying figures, which show:
- Fig. 1
- a schematic view of a tumble dryer with a heat pump system;
- Fig. 2
- a top view of the basement section of the tumble dryer,
- Fig. 3
- an enlarged detail view of
Fig. 2 in partial cross-section, - Fig. 4
- a cross-sectional side view of a detail of the basement section,
- Fig. 5
- a perspective view of the basement section of
Fig. 2 , - Fig. 6
- the bottom view of the basement section,
- Fig. 7
- a side view of the basement section partially opened,
- Fig. 8
- a second embodiment of a basement section of the dryer in simplified top view representation with components placed left and right to the center channel,
- Figs. 9 and 10
- a third and fourth embodiment of a basement section of the dryer in simplified top view representation with compressor shields in different arrangement,
- Fig. 11
- a fifth embodiment of a basement section of the dryer in simplified top view representation with heat pump components placed on the top of the heat pump battery, and
- Fig. 12
- a heat loss diagram for different operation modes of the heat pump system.
-
Fig. 1 depicts in a schematic representation ahome appliance 2 which in this embodiment is a heat pump tumble dryer. The tumble dryer comprises aheat pump system 4, including in a closed refrigerant loop in this order of refrigerant flow B: afirst heat exchanger 10 acting as evaporator (gas heater) for evaporating (heating) the refrigerant and cooling process air, acompressor 14, asecond heat exchanger 12 acting as condenser (gas cooler) for cooling the refrigerant and heating the process air, anauxiliary heat exchanger 34 acting as additional condenser, and anexpansion device 16 from where the refrigerant is returned to thefirst heat exchanger 10. Together with the refrigerant pipes connecting the components of theheat pump system 4 in series, the heat pump system forms arefrigerant loop 6 through which - in normal operation - the refrigerant is circulated by thecompressor 14 as indicated by arrow B. Theauxiliary condenser 34 dissipates heat to the ambient of thedryer 2 in the steady state of theheat pump system 4 in which maximum or nearly maximum operation condition is achieved after the warm-up period and the heat deposited by the compressor in therefrigerant loop 6 has to be removed viaauxiliary condenser 34 to prevent overheating. - The sequence of the components in the refrigerant loop can be modified in the embodiments herein in that the
auxiliary condenser 34 is not placed between thecondenser 12 and theexpansion device 16 with respect to refrigerant flow, but between thecompressor 14 and the condenser 12 (not shown). This modification is applicable to all embodiments herein. - The
expansion device 16 is a controllable valve that operates under the control of a control unit to adapt the flow resistance for the refrigerant in dependency of operating states of the heat pump system. In alternative embodiments theexpansion device 16 can be a capillary tube, a valve with fixed expansion cross-section, a throttle valve with variable cross section that automatically adapts the expansion cross-section in dependency of the refrigerant pressure (e.g. by elastic or spring biasing), a semi-automatic throttle valve in which the expansion cross-section is adapted in dependency of the temperature of the refrigerant (e.g. by actuation of a thermostat and/or where the temperature of the refrigerant is taken between the gas cooler and the gas heater, the gas heater and the compressor, or the compressor and the gas cooler), or the like. - The process air flow within the
home appliance 2 is guided through acompartment 18 of thehome appliance 2, i.e. through acompartment 18 for receiving articles to be treated, e.g. adrum 18. The articles to be treated are textiles,laundry 19, clothes, shoes or the like. In the embodiments here these are preferably textiles, laundry or clothes. The process air flow is indicated by arrows A inFig. 1 and is driven by aprocess air blower 8. Outside thedrum 18 the process air A is guided through anair channel 20. The air exiting thedrum 18 through the drum outlet (which is the loading opening of the drum) is filtered by afirst fluff filter 22 arranged close to the drum outlet in or at thechannel 20. Then the air flows through asecond fluff filter 24 arranged close to thefirst heat exchanger 10, through thefirst heat exchanger 10, through thesecond heat exchanger 12 and is guided back through an or a plurality of openings in the backside ofdrum 18 into the drum. Thus a closed process air loop is formed. - When the
heat pump system 4 is operating in the equilibrium or a normal mode (after the warm-up period i.e. after starting theheat pump system 4 from ambient temperature state), thefirst heat exchanger 10 transfers heat from the process air to the refrigerant. By cooling the process air to lower temperatures, humidity from the process air condenses at thefirst heat exchanger 10, is collected there and the collected condensate is drained to acondensate collector 30. The process air cooled and dehumidified when passing the first heat exchanger passes then through thesecond heat exchanger 12 where heat is transferred from the refrigerant to the process air. The process air is sucked fromexchanger 12 by theblower 8 and driven into thedrum 18 where it heats up thelaundry 19 and receives the humidity therefrom. - The main components of the
heat pump system 4 are arranged in abase section 5 or basement of thedryer 2, different embodiments of which are shown in the following figures. Theprocess air channel 20 guides the process air flow A outside thedrum 18 and includes different sections, including the section forming thebattery channel 20a in which the first andsecond heat exchangers second heat exchanger 12 flows into arear channel 20b in which theprocess air blower 8 is arranged. The air conveyed byblower 8 is guided upward in a risingchannel 20c to the backside of thedrum 18. - In the prior art it is known to blow ambient air for cooling through an auxiliary condenser and then to the compressor or ambient air is blown only to the compressor for cooling. Therein a cooling blower is intermittently switched ON/OFF by a thermostat if the refrigerant exceeds a critical temperature. This intermittent operation results in a cyclic increase and decrease of the operation temperature of the compressor and the refrigerant in the refrigerant loop. The time diagram in
Fig. 12 shows by curve D the time behavior of the heat loss factor for a conventional heat pump tumble dryer in which an auxiliary condenser and the compressor are cooled in such an ON/OFF cycle. E shows the respective time behavior for thedryer 2 according to the invention in which theheat pump system 4 is cooled using only or essentially theauxiliary condenser 34 for removing the excessive heat during the steady state after the warm-up period. As soon as the steady state has been achieved or is approached, a coolingair blower 28 is activated and continuously operated during the steady phase without cooling down thecompressor 14. - Curves E and D indicate the heat loss factor which is defined as unity (1) minus the ratio between the power given to the fluid by the compressor (Pcooling) and the electric power adsorbed by the compressor (Pcompressor). I.e. the shown heat loss factor = 1 - Pcooling/Pcompressor. In other words, the heat loss factor is the percentage of the power adsorbed by the compressor that is lost as heat losses. Of course, the lower this value, the better for the system efficiency. From
Fig. 12 it is clear that continuous operation of theblower 28 and keeping the compressor at constant temperature is advantageous over the operation mode in prior art heat pump systems. - According to the preferred embodiment of the invention when reaching or approaching the steady state the cooling
air blower 28 is activated and continuously operated. Thus the cooling capacity of theauxiliary condenser 34 is fully used (as compared to the conventional intermittent operation) and the cooling capacity of theauxiliary condenser 34 can be reduced. - Due to the improved efficiency as shown by
Fig. 12 the energy efficiency is also improved. -
Fig. 2 shows a top view of theheat pump system 4 of thedryer 2 arranged in thedryer base section 5. The base section is housing the heat pump system and parts of theprocess air channel 20 in abottom shell 40 forming the base frame of the dryer and having the dryer foots (compareFig. 6 ). Acover shell 42 is placed over thebottom shell 40, wherein portions of both shells form thebattery channel 20a in which the first andsecond heat exchanger 10, 12 (which form the battery of the heat pump system) are encased. Therear channel 20b and theblower 8 are also encased by bottom andtop shell Fig. 2 the reference numerals partially (e.g. 8, 10 and 12) have been placed at or over section of thetop shell 42 where the component covered by the top shell actually can not be seen, but its location is indicated thereby. Themotor 9 for drivingblower 8 and thedrum 18 is also located under thecover shell 42 and in this embodiment is located betweenblower 8 andcompressor 14. - In front of the inlet of the
first heat exchanger 10 thesecond fluff filter 24 is placed in a drawer inserted into the lower part of theprocess air channel 20. The condensate water that is condensing at thefirst heat exchanger 10 is collected in a tray formed below theexchanger 10 in thebottom shell 40 and is guided in a condensate channel at the side of thesecond heat exchanger 12 into thecondensate collector 30 formed by a rear section of thebottom shell 40. A level sensor and a condensate pump are arranged at thecollector 30 to pump the condensate to a condensate reservoir at the top of the dryer. - The
auxiliary condenser 34 is placed in an upright orientation in thebottom shell 40 such that its slender top side is seen inFig. 2 . At the front side of thecondenser 34 the coolingair blower 28 is arranged which sucks in ambient air through openings in thebottom shell 40 at the basement front side of thedryer 2. The conveyed cooling air passes through thecondenser 34 from the lower side as shown inFig. 2 and exits at the upper side thecondenser 34 which is the rear side of the condenser when seen from front of the dryer. The cooling air exiting thecondenser 34 is guided downward by adeflector shield 36 placed immediately behind the condenser, facing its rear or exit side. -
Fig. 3 shows in cross-section an enlarged section of the lower right side ofFig. 2 where theauxiliary condenser 34 is placed. The radiator rips ofcondenser 34 can be seen arranged around the zigzag or meander-shaped refrigerant pipe. As can be seen from the cross-section, there is a gap between theauxiliary condenser 34 and thedeflector shield 36 such that the cooling air that has passed thecondenser 34 can flow through the gap.Shield 36 has aside shield 37 that is running at both lateral sides partially over the depth of condenser 34 (the depth direction is the cooling air passing direction) and completely over the top side of the condenser. The partialside shield portions 37 can be seen in cross section inFig. 3 and the topside shield portion 37 can be seen in the top view ofFig. 2 . The shield is enclosing the rear side, partial lateral side and top side ofcondenser 34 and is open towards the front side (condenser air inlet) and bottom side (air outlet). -
Fig. 4 is a lateral cross section of a part of thebase section 5 in the region of thecondenser 34 along a cross section line from the front of the dryer (left side inFig. 4 ) towards the rear side of the dryer. Dashed arrow C indicates the cooling or ambient air flow conveyed byblower 28 through theauxiliary condenser 34 and deflected at its backside downward by thedeflector shield 36. The air flow C exits thebase section 5 throughopenings 38 formed in thebottom shell 40. Theopenings 38 can be seen in more detail in the view from below inFig. 6 . -
Fig. 5 shows a perspective view to thebase section 5 with thecover shell 42, second fluff filter 24 (drawer),blower 8 andmotor 9 removed. - In
Fig. 7 the lateral side view of thebase section 5 is shown completely as compared toFig. 4 . Thecover shell 42 is placed in position and over themotor 9 section ofcover shell 42 thepower converter 44 for the compressor 14 (and/or other power electronics) is mounted. As a modification of the embodiment shown inFigs. 1 to 6 a branchingchannel 46 is provided as schematically shown inFig. 7 . The branchingchannel 46 has a cooling air inlet at thedeflector shield 36 and an outlet to the housing encasing thepower electronics 44. As soon as theblower 28 is activated, a portion of the ambient air that passed theauxiliary condenser 34 is guided to thepower electronics 4 for cooling it. -
Figs. 8 to 11 show as schematic view the arrangement of heat pump components in thebase section 5 in top view according to other embodiments. The same reference numerals for components of theheat pump system 4 operating the same way as the components inFigs. 1 to 7 are used. For simplicity reference is made to the above and deviating implementations are indicated below. - In the embodiment of
Fig. 8 in thebase section 5 theblower 8, drum andblower motor 9 andcompressor 14 are arranged on a first side of thebattery channel 20a, and theblower 28, thecondenser 34 and thepower electronics 44 are arranged on a second side of thebattery channel 20a. Thebattery channel 20a is forming a center or middle section of thebase section 5 running from a front region to the back region of thebase section 5. It provides a partition wall ordeflector shield 36a preventing a cooling or ambient air flow from the coolingair blower 28 to thecompressor 14. Optionally thepower electronics 44 is not arranged in the flow path of the cooling air. For example the power electronics is arranged above themotor 9 similarly as shown inFig. 7 . The cooling air flow C is sucked in byblower 28 through openings in the front region of thebase section 5, is pushed by theblower 28 through thecondenser 34 towardspower electronics 44, is deflected by the outer case of the condensate collector to the side and exits thebase section 5 through openings at a side wall thereof. In further embodiments ofFig. 8 the cooling air flow C is reversed and/or theblower 28 is arranged on the rear side of condenser 34 (when seen from the front of dryer 2). - It is to be noted that in the embodiment of
Fig. 8 the depth of the dryer may be decreased as compared to the 60 cm depth of a conventional dryer. For example the depth of such dryer type is maximum or less than 55 cm, 50 cm or 45 cm. By the depth reduction the volume of the drum is reduced at the same time while the drum diameter is full size adapted to the 60 cm width of conventional dryers. With reduced drum volume the required drying capacity is reduced and the dimension or capacity of the components of theheat pump system 4 can be reduced. Thus narrowing thebattery channel 20a width as indicated inFig. 8 is easily implemented. Such dryer is adapted for small apartment use or single/double household needs. - In the embodiment of
Fig. 9 thebattery channel 20a is arranged on the left side of thebase section 5. On the right side of the base section adeflector shield 36b is arranged between thecompressor 14 at one side and thecondenser 34 andblower 28 at the other side to prevent cooling air flow to the compressor. Theblower 28 sucks the cooling air flow C through openings on the left side of the base section and through theauxiliary condenser 34 and blows it against thepower electronics 44 and themotor 9. Exhaust of the air flow C is through openings on the lateral side and/or in the bottom of base section 5 (bottom shell 40). Optionally the flow direction of air flow C is reversed and/or the power electronics and/or themotor 9 are not in the cooling air flow path. - In the embodiment of
Fig. 10 the housing ofmotor 9 is arranged between the cooling air flow C and thecompressor 14 thus forming adeflector shield 36c. Theblower 28 sucks the cooling air through openings in thebottom shell 40 and pushes it through theauxiliary condenser 34 againstshield 36c which deflects the flow C through openings in the lateral side ofbase section 5. - In the embodiment of
Fig. 11 theauxiliary condenser 34,blower 28 andpower electronics 44 are placed on top and/or above thebattery channel 20a (containingevaporator 10 and condenser 12). Optionally thepower electronics 44 is not in the flow path of cooling air C and instead e.g. placed on the case of motor 9 (compareFig. 7 ). Adeflector shield 36d in the form of a cooling air channel wall is provided to guide the air flow C and prevent flowing it towardscompressor 14. The air flow enters through openings in the lateral side wall of the - in this case vertically extended - base section (preferably in the bottom shell 40), flows throughcondenser 44 and is pushed byblower 28 towards the power electronics (optional) and through openings at the backside of the base section. Preferably the coolingair channel 36d covers the lateral side and the top side of thecomponents channel 36d has openings not at the lateral side wall of the base section, but on the front side of thebase section 5. - The cooling
air channel 36d preferably is arranged on the outermost left side above the upper level of thebattery channel 20a and is preferably small in width as compared to thebattery channel 20a. Thereby the lowest point of thedrum 18 can be kept close to the upper side ofbattery channel 20a, while the dead space at the left side within the dryer body is used to arrange the cooling air channel. The same is true in an embodiment in which the cooling air channel is arranged at the outermost right side above the level of thebattery channel 20a and/or the case of themotor 9. Compare the position of thepower electronics 44 inFig. 7 - such that thechannel 36d takes the position ofelectronics 44 and preferably does not extend the complete depth of thebase section 5, e.g. by providing cooling air inlet or outlet openings at a lateral side or bottom side of the vertically extendedbase section 5. - In the embodiments the cooling
air blower 28 is depicted and arranged as axial blower (axial fan in which the air flow C enters and exits in the axial direction with respect to the blower rotation axis). However in the embodiments a radial blower (radial fan or centrifugal fan) or a tangential blower (cross-flow fan) can be used. If for example a radial blower is used, the backside wall of the radial blower (which is opposite to the inlet opening for the conveyed air) can at the same time represent the deflector shield (shielding device) that prevents air flow to thecompressor 14. Preferably if a radial blower is used asblower 28, in the embodiments the cooling air can be sucked through theauxiliary condenser 34 when the radial blower is arranged in the direction of the outlet side of thecondenser 34. The cooling air conveyed by the radial blower can then be exhausted into a direction perpendicular to the exit air direction (i.e. preferably the axial inlet direction of the radial blower). For example through openings in the bottom ofbottom shell 40. Specifically in the embodiment ofFigs. 2 to 7 the order ofauxiliary condenser 34 andblower 28 from front to rear can be changed such that thecondenser 34 is close to the front opening and the blower is on the backside ofcondenser 34 and exhausts the cooling air through theoutlet openings 38. In this way the radial blower with its housing replaces theaxial blower 28 and thedeflector shield 36. -
- 2
- tumble dryer
- 4
- heat pump system
- 5
- base section
- 6
- refrigerant loop
- 8
- process air blower
- 9
- blower + drum motor
- 10
- first heat exchanger (evaporator)
- 12
- second heat exchanger (condenser)
- 14
- compressor
- 16
- expansion device
- 18
- drum (laundry compartment)
- 19
- laundry
- 20
- air channel
- 20a
- battery channel
- 20b
- rear channel
- 20c
- rising channel
- 22
- first fluff filter
- 24
- second fluff filter
- 28
- cooling air blower
- 30
- condensate collector
- 34
- auxiliary condenser
- 36, 36a, 36b, 36c, 36d
- deflector shield
- 37
- side shield
- 38
- bottom openings
- 40
- bottom shell
- 42
- cover shell
- 44
- power converter
- 46
- branching channel
- A
- process air flow
- B
- refrigerant flow
- C
- ambient air flow
- D
- conventional heat loss
- E
- reduced heat loss
Claims (19)
- Laundry treatment apparatus (2), in particular dryer, washing machine or washing machine having drying function, comprising:a laundry storing chamber (18) for treating laundry using processing air (A),a blower (28) for blowing cooling air (C),a processing air loop for circulating the processing air (A) through the laundry storing chamber (18), anda heat pump system (4) for dehumidifying and heating the processing air (A), the heat pump system having a refrigerant loop (6), comprising:a first heat exchanger (10) for heating a refrigerant and cooling the processing air (A),a second heat exchanger (12) for cooling the refrigerant and heating the processing air (A),a refrigerant expansion device (16) arranged in the refrigerant loop (6) between the second heat exchanger (12) and the first heat exchanger (10),a compressor (14) arranged in the refrigerant loop (6) between the first heat exchanger (10) and the second heat exchanger (12), andan auxiliary heat exchanger (34) connected in the refrigerant loop (6) for cooling the refrigerant,wherein the blower (28) is adapted to remove heat from the auxiliary heat exchanger (34);characterized in thata shielding device (36, 36a-d) is arranged to shield the compressor (14) against cooling air (C) blown by the blower (28), and/orthe compressor (14) is insulated to prevent heat exchange with the compressor's ambient air and the cooling air (C).
- Apparatus according to claim 1, wherein the shielding device (36, 36a-d) is arranged between the compressor (14) and the auxiliary heat exchanger (34) and/or between the compressor (14) and the blower (28),
- Apparatus according to claim 1 or 2, wherein the shielding device (36, 36a-d) is or comprises a partition wall, a shell and/or a process air duct section (20a) in which the first and second heat exchangers (10, 12) are arranged.
- Apparatus according to claim 1, 2 or 3, wherein the air flow shielding device (36, 36a-d) deflects the cooling air flow (C) and/or wherein the air flow shielding device (36, 36a-d) deflects the cooling air flow (C) to an outlet in the bottom (40) and/or side wall of the apparatus cabinet.
- Apparatus according to claim 1, wherein a power electronics (44) of the apparatus is part of the flow shielding device and/or wherein the laundry storing chamber (18) is a rotatable drum and a drum driving motor (9) is part of the flow shielding device (36c).
- Apparatus according to any of the previous claims, wherein the auxiliary heat exchanger (34) has a cooling air inlet, a cooling air outlet and a major flow path for the cooling air (C) through the auxiliary heat exchanger, and wherein the air flow shielding device (36, 36b, 36c) shields and/or deflects the cooling air flow away from the direction of the major flow path at the cooling air outlet of the auxiliary heat exchanger.
- Apparatus according to any of the previous claims, wherein the air flow shielding device (36, 36a-d) shields the cooling air flow (C) at one, two or three lateral sides (37) of the auxiliary heat exchanger (34), wherein the lateral sides are lateral of the auxiliary heat exchanger with respect to the cooling air outlet or a major flow path of cooling air through the auxiliary heat exchanger.
- Apparatus according to any of the previous claims, comprising a cooling air duct (46) to guide at least a portion of the cooling air flow blown by the blower (28) to a power electronics (44) of the apparatus.
- Apparatus according to claim 8, wherein the inlet or outlet of the cooling air duct (46) is arranged at the air flow shielding device (36, 36a-d).
- Apparatus according to any of the previous claims, wherein the laundry storing chamber (18) is a rotatable drum and the apparatus comprises a motor (9) for driving the drum, wherein the cooling air blown by the blower (28) is blown to the drum driving motor (9) and/or to a power electronics (44).
- Apparatus according to any of the previous claims,
wherein the first and second heat exchangers (10, 12) are arranged in a process air duct section (20a) of the processing air loop which is located in a middle section of the base section (5) of the apparatus,
wherein the blower (28) and the auxiliary heat exchanger (34) are arranged at a first side of the middle section, and
wherein the compressor (14) is arranged at a second side of the middle section opposite to the first side. - Apparatus according to claim 11, wherein additionally a drum motor (9) and/or power electronics (44) is arranged at the second side.
- Apparatus according to any of claims 1 to 10, wherein the auxiliary heat exchanger (34) and/or the blower (28) are arranged at a height level in the apparatus above the first and second heat exchanger (10, 12).
- Apparatus according to any of the previous claims, wherein
the blower (28) is blowing the cooling air (C) towards the auxiliary heat exchanger (34) or is sucking the cooling air from the auxiliary heat exchanger, and/or
the blowing direction of cooling air (C) blown by the blower (28) is perpendicular or parallel to a process air duct section (20a) of the processing air loop in which the first and second heat exchanger (10, 12) are arranged. - Apparatus according to any of the previous claims, wherein
the auxiliary heat exchanger (34) has a cooling power in the range from 100 to 500 W, 150 to 450 W or 200 to 450 W, and/or
the auxiliary heat exchanger (34) is adapted to reduce the refrigerant temperature by 4 to 18°C, 5 to 15°C, 8 to 13°C or 10 to 15°C. - Apparatus according to any of the previous claims, wherein the auxiliary heat exchanger (34) is arranged in the refrigerant loop (6) between the second heat exchanger (12) and the refrigerant expansion device (16) or between the compressor (14) and the second heat exchanger (12).
- Apparatus according to any of the previous claims, wherein the blower (28) has a conveyance capacity in the range of 30 to 200 m3/h, 50 to 180 m3/h or 100 to 150 m3/h.
- Apparatus according to any of the previous claims, wherein the apparatus further comprises a control unit and wherein the control unit is adapted
to control at least one laundry treatment process,
to start the blower (28) as soon as a refrigerant pressure and/or temperature in the refrigerant loop (6) and/or processing air temperature has exceeded or is approaching a predefined value(s), and
to continuously operate the blower (28) throughout the running laundry treatment process. - Apparatus according to claim 18, wherein, after starting the blower (28), the control unit is adapted to operate the blower with a constant speed or with a blower speed that is varied in a range around an average, non-zero speed, wherein the range is less than ± 30%, ± 20% or ± 10% of the average speed.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP11174963.6A EP2549007B1 (en) | 2011-07-22 | 2011-07-22 | Heat pump laundry treatment apparatus |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP11174963.6A EP2549007B1 (en) | 2011-07-22 | 2011-07-22 | Heat pump laundry treatment apparatus |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2549007A1 true EP2549007A1 (en) | 2013-01-23 |
EP2549007B1 EP2549007B1 (en) | 2020-02-26 |
Family
ID=44582271
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11174963.6A Active EP2549007B1 (en) | 2011-07-22 | 2011-07-22 | Heat pump laundry treatment apparatus |
Country Status (1)
Country | Link |
---|---|
EP (1) | EP2549007B1 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2801654A1 (en) * | 2013-05-07 | 2014-11-12 | Miele & Cie. KG | Laundry dryer with drum which is mounted so as to be rotatable in a housing |
JP2015198872A (en) * | 2014-04-10 | 2015-11-12 | 株式会社Tosei | dryer |
EP2990524A1 (en) * | 2014-08-29 | 2016-03-02 | Electrolux Appliances Aktiebolag | Heat pump laundry dryer |
WO2018001158A1 (en) * | 2016-06-27 | 2018-01-04 | 青岛海尔滚筒洗衣机有限公司 | Method for regulating quantity of condensing mediums according to change in air temperature of egress cylinder of clothes dryer |
EP2650425B1 (en) * | 2012-04-12 | 2018-11-21 | Electrolux Home Products Corporation N.V. | Laundry drying machine |
EP3992351A4 (en) * | 2019-09-04 | 2022-08-24 | Samsung Electronics Co., Ltd. | Clothes dryer |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4409607A1 (en) | 1993-04-21 | 1994-10-27 | Miele & Cie | Condensation-type laundry drier with a heat pump |
DE4434205A1 (en) * | 1994-08-31 | 1996-03-07 | Joerg Sdrojewski | Laundry dryer with laundry drum |
DE202006018205U1 (en) * | 2006-11-06 | 2007-02-15 | V-Zug Ag | Clothes dryer with a drum and a heat pump circuit comprising a condenser, a throttle, an evaporator and a compressor comprises an auxiliary heat exchanger between the condenser and the throttle |
EP1811077A1 (en) * | 2006-01-20 | 2007-07-25 | SANYO ELECTRIC Co., Ltd. | Drying machine |
WO2008073008A1 (en) * | 2006-12-11 | 2008-06-19 | Tes Scandinavia Ab | Improved drying device |
US7458171B1 (en) * | 2007-01-29 | 2008-12-02 | Lentz Luke E | Dehumidifier clothes dryer apparatus |
-
2011
- 2011-07-22 EP EP11174963.6A patent/EP2549007B1/en active Active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4409607A1 (en) | 1993-04-21 | 1994-10-27 | Miele & Cie | Condensation-type laundry drier with a heat pump |
DE4434205A1 (en) * | 1994-08-31 | 1996-03-07 | Joerg Sdrojewski | Laundry dryer with laundry drum |
EP1811077A1 (en) * | 2006-01-20 | 2007-07-25 | SANYO ELECTRIC Co., Ltd. | Drying machine |
DE202006018205U1 (en) * | 2006-11-06 | 2007-02-15 | V-Zug Ag | Clothes dryer with a drum and a heat pump circuit comprising a condenser, a throttle, an evaporator and a compressor comprises an auxiliary heat exchanger between the condenser and the throttle |
WO2008073008A1 (en) * | 2006-12-11 | 2008-06-19 | Tes Scandinavia Ab | Improved drying device |
US7458171B1 (en) * | 2007-01-29 | 2008-12-02 | Lentz Luke E | Dehumidifier clothes dryer apparatus |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2650425B1 (en) * | 2012-04-12 | 2018-11-21 | Electrolux Home Products Corporation N.V. | Laundry drying machine |
EP2801654A1 (en) * | 2013-05-07 | 2014-11-12 | Miele & Cie. KG | Laundry dryer with drum which is mounted so as to be rotatable in a housing |
JP2015198872A (en) * | 2014-04-10 | 2015-11-12 | 株式会社Tosei | dryer |
EP2990524A1 (en) * | 2014-08-29 | 2016-03-02 | Electrolux Appliances Aktiebolag | Heat pump laundry dryer |
WO2016030149A1 (en) * | 2014-08-29 | 2016-03-03 | Electrolux Appliances Aktiebolag | Heat pump laundry dryer |
CN106661815A (en) * | 2014-08-29 | 2017-05-10 | 伊莱克斯家用电器股份公司 | Heat pump laundry dryer |
WO2018001158A1 (en) * | 2016-06-27 | 2018-01-04 | 青岛海尔滚筒洗衣机有限公司 | Method for regulating quantity of condensing mediums according to change in air temperature of egress cylinder of clothes dryer |
US11053634B2 (en) | 2016-06-27 | 2021-07-06 | Qingdao Haier Drum Washing Machine Co., Ltd. | Method for regulating quantity of condensing medium according to change in air temperature at outlet of barrel of dryer |
EP3992351A4 (en) * | 2019-09-04 | 2022-08-24 | Samsung Electronics Co., Ltd. | Clothes dryer |
Also Published As
Publication number | Publication date |
---|---|
EP2549007B1 (en) | 2020-02-26 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
AU2012314534B2 (en) | Laundry treatment apparatus with heat pump | |
US20240183100A1 (en) | Clothes treating apparatus having drying function | |
AU2012289035B2 (en) | Basement arrangement in heat pump laundry treatment apparatus | |
US9803312B2 (en) | Dryer with heat pump | |
EP2549007B1 (en) | Heat pump laundry treatment apparatus | |
CN104884701B (en) | The method of heat pump clothes treatment device and operation heat pump clothes treatment device | |
EP2573253B1 (en) | Heat pump dryer | |
US11060236B2 (en) | Dryer appliance and method of operating the same based on the relative humidity of drum exit air | |
AU2014234494A1 (en) | Laundry treatment apparatus with heat pump | |
EP2097579B1 (en) | A washer/dryer | |
JP7319028B2 (en) | clothes dryer | |
EP4219822A1 (en) | Dryer with high air tigthness of a process air circuit and process for operating the dryer | |
EP4219823A1 (en) | Dryer with improved air tigthness of a process air circuit and process for operating the dryer | |
JP2021045331A (en) | Clothes dryer | |
CN112779741A (en) | Drying apparatus |
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 |
|
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 |
|
17P | Request for examination filed |
Effective date: 20130723 |
|
RBV | Designated contracting states (corrected) |
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 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: EXAMINATION IS IN PROGRESS |
|
17Q | First examination report despatched |
Effective date: 20181009 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
INTG | Intention to grant announced |
Effective date: 20190924 |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: NOVIELLO, FLAVIO Inventor name: BISON, ALBERTO Inventor name: CAVARRETTA, FRANCESCO |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 1237745 Country of ref document: AT Kind code of ref document: T Effective date: 20200315 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602011065186 Country of ref document: DE |
|
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: 20200226 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: 20200526 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: 20200226 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20200226 |
|
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: 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: 20200526 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: 20200226 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: 20200527 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: 20200226 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: 20200626 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: 20200226 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20200226 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20200226 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: 20200226 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: 20200719 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: 20200226 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: 20200226 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: 20200226 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: 20200226 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: 20200226 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: 20200226 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 1237745 Country of ref document: AT Kind code of ref document: T Effective date: 20200226 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602011065186 Country of ref document: DE |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20200226 |
|
26N | No opposition filed |
Effective date: 20201127 |
|
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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20200226 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: 20200226 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: 20200226 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20200722 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20200731 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200731 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200731 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200722 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200731 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200722 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200731 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200722 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20200226 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: 20200226 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: 20200226 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20200226 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: 20200226 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20220726 Year of fee payment: 12 Ref country code: DE Payment date: 20220720 Year of fee payment: 12 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230625 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 602011065186 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20240201 |