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
  • D06F33/00—Control of operations performed in washing machines or washer-dryers 
  • D06F33/30—Control of washing machines characterised by the purpose or target of the control 
  • D06F33/46—Control of the energy or water consumption
• • A—HUMAN NECESSITIES
  • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
  • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
  • A47L15/00—Washing or rinsing machines for crockery or tableware
  • A47L15/0018—Controlling processes, i.e. processes to control the operation of the machine characterised by the purpose or target of the control
  • A47L15/0047—Energy or water consumption, e.g. by saving energy or water
• • A—HUMAN NECESSITIES
  • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
  • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
  • A47L15/00—Washing or rinsing machines for crockery or tableware
  • A47L15/42—Details
  • A47L15/4214—Water supply, recirculation or discharge arrangements; Devices therefor
  • A47L15/4219—Water recirculation
• • A—HUMAN NECESSITIES
  • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
  • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
  • A47L15/00—Washing or rinsing machines for crockery or tableware
  • A47L15/42—Details
  • A47L15/4291—Recovery arrangements, e.g. for the recovery of energy or water
• • 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
  • D06F39/00—Details of washing machines not specific to a single type of machines covered by groups D06F9/00 - D06F27/00 
  • D06F39/04—Heating arrangements
• • 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
  • D06F39/00—Details of washing machines not specific to a single type of machines covered by groups D06F9/00 - D06F27/00 
  • D06F39/08—Liquid supply or discharge arrangements
  • D06F39/083—Liquid discharge or recirculation arrangements
• • A—HUMAN NECESSITIES
  • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
  • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
  • A47L15/00—Washing or rinsing machines for crockery or tableware
  • A47L15/42—Details
  • A47L15/4202—Water filter means or strainers
• • A—HUMAN NECESSITIES
  • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
  • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
  • A47L2401/00—Automatic detection in controlling methods of washing or rinsing machines for crockery or tableware, e.g. information provided by sensors entered into controlling devices
  • A47L2401/03—Operation mode, e.g. delicate washing, economy washing, reduced time, sterilizing, water softener regenerating, odor eliminating or service
• • A—HUMAN NECESSITIES
  • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
  • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
  • A47L2501/00—Output in controlling method of washing or rinsing machines for crockery or tableware, i.e. quantities or components controlled, or actions performed by the controlling device executing the controlling method
  • A47L2501/06—Water heaters
• • A—HUMAN NECESSITIES
  • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
  • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
  • A47L2501/00—Output in controlling method of washing or rinsing machines for crockery or tableware, i.e. quantities or components controlled, or actions performed by the controlling device executing the controlling method
  • A47L2501/36—Other output
• • 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
  • D06F2103/00—Parameters monitored or detected for the control of domestic laundry washing machines, washer-dryers or laundry dryers
  • D06F2103/68—Operation mode; Program phase
• • 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
  • D06F2105/00—Systems or parameters controlled or affected by the control systems of washing machines, washer-dryers or laundry dryers
  • D06F2105/26—Heat pumps
• • 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
  • D06F23/00—Washing machines with receptacles, e.g. perforated, having a rotary movement, e.g. oscillatory movement, the receptacle serving both for washing and for centrifugally separating water from the laundry 
  • D06F23/02—Washing machines with receptacles, e.g. perforated, having a rotary movement, e.g. oscillatory movement, the receptacle serving both for washing and for centrifugally separating water from the laundry  and rotating or oscillating about a horizontal axis
• • 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
  • D06F25/00—Washing machines with receptacles, e.g. perforated, having a rotary movement, e.g. oscillatory movement, the receptacle serving both for washing and for centrifugally separating water from the laundry and having further drying means, e.g. using hot air 

Definitions

• Articles Treatment Appliance for treating articles and Method for operating such Articles Treatment Appliance
• the present invention relates to an articles treatment appliance for treating articles with washing liquid, in particular a domestic laundry or dishes treatment machine and to a method for operating such treatment appliance.
• a first operation mode for heating washing liquid and a second operation mode for cooling the washing liquid are implemented.
• EP 3 135 799 Al suggests a washing machine using an evaporator and a condenser of a heat pump for heating and cooling the washing water during a washing cycle.
• the refrigerant flow direction can be reversed by a switching device.
• an articles treatment appliance for treating articles with washing liquid in particular a domestic laundry or dishes treatment machine, more preferably a washing machine, a washer dryer, or a dishwasher.
• the treatment appliance comprises a cabinet, a heat pump having: a compressor conveying refrigerant through a refrigerant loop, a first heat exchanger, in particular an evaporator, a second heat exchanger, in particular a condenser, an expansion arrangement arranged between the first heat exchanger and the second heat exchanger and being adapted to expand the refrigerant, and a refrigerant flow changing device adapted to change the refrigerant flow direction between a first flow direction and a second flow direction in at least a portion of the heat pump.
• the appliance further comprises a control unit adapted to operate the treatment appliance and to switch the refrigerant flow changing device to a first operation mode of the heat pump such that the refrigerant is flowing in the first flow direction and to a second operation mode of the heat pump such that the refrigerant is flowing in the second flow direction.
• the second heat exchanger In the first operation mode, the second heat exchanger is adapted to heat a washing liquid and the first heat exchanger is adapted to cool the heat exchanging medium, and in the second operation mode, the second heat exchanger is adapted to cool washing liquid and the first heat exchanger is adapted to heat the heat exchanging medium.
• the control unit is adapted to apply a first control characteristic in the first operation mode and a second control characteristic in the second operation mode, wherein the first and second control characteristics are different from each other, and wherein the first and second control characteristics are applied to one or more of:
• control characteristic for the speed and/or power of the compressor being a variable speed compressor
• control characteristic for controlling the opening state of the expansion arrangement comprising a controllable expansion valve.
• the first operation mode is a heating mode in which the washing liquid is heated by the refrigerant flowing through the second heat exchanger (e.g. condenser), and preferably the second operation mode is a defrosting (regeneration) mode in which the heat exchanging medium is heated by the refrigerant flowing through the first heat exchanger (e.g. evaporator).
• the heat exchanging medium is cooled and may freeze at least partially.
• the second operation mode is preferably used after the first operation mode to deice the heat exchanging medium. Therefore, an efficient and reliable working of the heat pump in the next heating mode may be ensured.
• the heat pump working conditions during each of the first and second operation modes and between the first and second operation modes may differ.
• the first control characteristic for the first operation mode and the second control characteristic for the second operation mode being different from the first control characteristic are required.
• the different control characteristics may comprise different 'conditions of the refrigerant loop', such as the inner volume and/or the tube diameter and/or the tube length and/or the heat exchanging capacity of the second heat exchanger (e.g. condenser) and the first heat exchanger (e.g. evaporator), which may be different.
• the second heat exchanger e.g. condenser
• the first heat exchanger e.g. evaporator
• the temperature of the washing liquid and/or of the heat exchanging medium at the start of both modes may be different.
• the temperature of the heat exchanging medium is e.g. less than 0° and the temperature of the washing liquid is e.g. at least 30°C.
• different working conditions of the heat pump e.g. different temperatures and/or pressures of the refrigerant and/or refrigerant flow rates
• different working conditions of the heat pump e.g. different temperatures and/or pressures of the refrigerant and/or refrigerant flow rates
• the efficiency of the heat pump may be increased in both operation modes.
• the heat pump may be adjusted to the different heat pump working conditions in the second operation mode, such as temperatures and/or pressures and/or flow rates of the refrigerant.
• the efficiency of the heat pump, and in particular of the second operation mode of the heat pump can be increased.
• the compressor being a variable speed compressor (VSC) may adjust the refrigerant flow rate by adjusting the speed and/or the power of the VSC.
• VSC variable speed compressor
• the refrigerant flow rate may be adjusted by the VSC in dependency of the first and/or second operation modes.
• the VSC may set a refrigerant flow rate in the first operation mode which is at least partially different to the refrigerant flow rate in the second operation mode.
• the refrigerant temperature may e.g. be detected at the inlet of the compressor, in particular between the compressor inlet and the refrigerant flow changing device).
• control unit is adapted to apply the first control characteristic to the compressor during the first operation mode in which or such that the compressor speed and/or the compressor power and/or the refrigerant pressure at the inlet of the compressor and/or the refrigerant temperature at the inlet of the compressor is (preferably generally) lower than when the control unit applies the second control characteristic.
• the second heat exchanger working as condenser may heat up the washing liquid to at least 20, 30, 35 or 40°C which requires that the refrigerant temperature is at or above this heating temperature.
• the heat exchanging medium may only be heated up to maximum 10, 15, 20, 25 or 30°C such that the refrigerant temperature must be only at or slightly above that temperature. Therefore the compression work by the compressor can or is kept much lower during the second operation mode which reduces significantly the energy consumption during the second operation mode.
• the first heat exchanger is arranged within a tank filled with a heat exchanging medium such as water.
• the temperature of the heat exchanging medium is preferably at a level that ensures a subsequent washing process to be performed.
• the temperature of the heat exchanging medium may be in the range of 10-20°C, 15-25°C or 20-30°C.
• the expansion arrangement may comprise one or more expansion valves.
• Flowing in a different flow path section of the refrigerant loop than in the second operation mode' may mean that in the first and second operation modes the refrigerant may flow at least partially along the same sections of the refrigerant loop, but that there may also be sections through which the refrigerant only flows in the first or the second operation mode (i.e. refrigerant loops in the first and second operation modes are at least partially different).
• controllable expansion valve is adapted to be controlled by the control unit of the appliance.
• the treatment appliance comprises a filter arrangement for filtering water and/or impurities dispersed in the refrigerant, wherein preferably the filter arrangement is arranged upstream of the expansion arrangement in the first and second operation mode and/or wherein preferably the filter arrangement comprises one or two monodirectional and/or bi-directional filter(s).
• Water may disperse in the refrigerant due to humidity entrapped inside the circuit when it is produced and loaded with gas.
• Impurities and/or solid material may disperse in the refrigerant due to refrigerant level of purity (the higher the purity the higher the cost of refrigerant), and/or due to the pipe welding process.
• the filter arrangement may avoid impurities or water, that may freeze or block the expansion arrangement, and/or avoid that water and impurities reach the compressor. Thus, a reliable operation of the heat pump may be ensured by providing the filter arrangement.
• the bi-directional filter enables refrigerant flow in both directions.
• the bi-directional filter preferably has internally different flow paths for the first and second operation mode. Thus, debris and impurities collected within the filter in the first operation mode is prevented from being washed out, when the refrigerant flows through the bidirectional filter in an opposite direction in the second operation mode.
• the refrigerant in the first operation mode is directed along a first refrigerant flow path section, and in the second operation mode the refrigerant is directed along a second refrigerant flow path section, wherein the first and second refrigerant flow path sections share a common flow path section in which the expansion arrangement is arranged, or wherein the expansion arrangement comprises a first expansion device arranged in a first non- shared flow path section of the first refrigerant flow path section and a second expansion device arranged in a second non- shared flow path section of the second refrigerant flow path section.
• Valves such as check valves or on/off valves may be arranged in the first and second refrigerant flow path.
• the control unit may be adapted to control the valves such that the refrigerant is directed along the first or the second refrigerant flow path section.
• the refrigerant in the first operation mode the refrigerant is directed through the first expansion device (or expansion element) and in the second operation mode the refrigerant is directed through the second expansion device.
• the flow direction through the expansion device arranged in the common flow path is the same in the first and second operation modes.
• the expansion element may be a fixed capillary or expansion valve or a variable expansion valve or a thermostatic expansion valve or a (preferably electronically) controllable expansion valve with a controllable flow or expansion rate.
• the compressor of the appliance is a variable speed compressor.
• the compressor is a variable speed compressor.
• the fixed expansion device is e.g. an expansion valve which is not controllable, i.e. the refrigerant flow rate in the first and second operation modes is fixed, respectively.
• the refrigerant in the first operation mode the refrigerant is directed along a or the first refrigerant flow path section and in the second operation mode the refrigerant is directed along a or the second refrigerant flow path section, and the first and second refrigerant flow path sections share a or the common flow path section in which a or the filter of the filter arrangement is arranged, or a first filter of the filter arrangement is arranged in a or the first non-shared flow path section and a second filter is arranged in a or the second non-shared flow path section.
• the filters are preferably monodirectional filters.
• the first and/or second filter are arranged upstream a commonly shared expansion device (which is preferably arranged in the commonly shared section or the first and second non-shared flow path section may be joined at the commonly shared expansion device) or are each arranged upstream an expansion device each arranged in a non-shared section of the flow path sections.
• a commonly shared expansion device which is preferably arranged in the commonly shared section or the first and second non-shared flow path section may be joined at the commonly shared expansion device
• the expansion arrangement comprises a bi-directional expansion device preferably having a different flow characteristic when the refrigerant passes in the first or the second direction through the expansion device.
• the flow rate and/or flow resistance and/or expansion work of the expansion device is different for the first and second direction.
• the flow characteristic being different in dependency of the flow direction may be provided in that the bi-directional expansion device has an internal structure configured such that the flow characteristic (e.g. the flow rate when having identical inlet/outlet pressure and temperature) is different for the different flow directions.
• the control unit is adapted to apply a different control characteristic to the bi-directional expansion device in dependency of the first or second operation mode.
• the bi-directional expansion device is a thermostatic expansion device and the temperature probe (and optionally the pressure probe) of the expansion device is arranged at a position of the refrigerant loop where the temperature (and optionally the pressure) is basically different when detected in the first or second operation mode, e.g. the probe(s) is(are) arranged at a position where the refrigerant flow direction is reverted.
• a first bi-directional filter is arranged upstream of the bidirectional expansion device in a common flow path of the first and second refrigerant flow path sections and a second bi-directional filter is arranged downstream of the bidirectional expansion device in a common flow path of the first and second refrigerant flow path sections. Therefore, the refrigerant is filtered in the first and second operation mode before flowing through the expansion device.
• the appliance further comprises flow rectifier means which passes the refrigerant through a or the first refrigerant flow path section in the first operation mode and through a or the second refrigerant flow path section in the second operation mode.
• flow rectifier means which passes the refrigerant through a or the first refrigerant flow path section in the first operation mode and through a or the second refrigerant flow path section in the second operation mode.
• the flow rectifier means comprises two, three or four check valves.
• 'Check valve' means any element adapted to pass the refrigerant flow only in one flow direction while blocking the flow in the opposite direction.
• the 'check valve' or one or more out of a plurality of 'check valves' may be formed as controllable valves that are opened and closed under the control of the control unit such that the same rectifying effect is achieved as by a check valve in the conventional meaning.
• the flow rectifier means is arranged as a bridge rectifier arrangement and wherein the first and second flow path sections have a or the common flow path section in which the refrigerant flows in the same direction independent of the first and second operation mode, and non-shared flow path sections in which the refrigerant only flows either in the first or in the second operation mode.
• the bridge rectifier arrangement is formed for example by using four check valves.
• one or more of the following are arranged in series: - the expansion arrangement, in particular a capillary, a bi-directional expansion device, a thermostatic expansion device, or an electric expansion device,
• the filter arrangement wherein in particular the filter arrangement is arranged upstream the expansion arrangement.
• one or more of the following are arranged in series:
• the expansion arrangement in particular a capillary, a bi-directional expansion device, a thermostatic expansion device, or an electric expansion device,
• the filter arrangement wherein in particular the filter arrangement is arranged upstream the expansion arrangement, and/or the filter arrangement comprises a bi-directional filter.
• the filter arrangement and the expansion arrangement are arranged in each of the non-shared flow path sections.
• the refrigerant flows in the first operation mode through a different filter arrangement and expansion arrangement as in the second operation mode. Therefore, the efficiency of both modes may be increased as each expansion arrangement may be adapted to the heat pump conditions of each operation mode.
• the treatment appliance further comprises a temperature sensor and/or a pressure sensor for detecting a temperature and/or pressure of the refrigerant in the heat pump, wherein more preferably the temperature sensor is arranged at an inlet of the compressor or upstream of the compressor.
• the temperature sensor may be arranged between the compressor inlet and an outlet of the first heat exchanger and/or an outlet of the refrigerant flow changing device.
• one temperature sensor may be arranged at the outlet of the second heat exchanger (in the first operation mode), and/or one temperature sensor at an inlet of the first heat exchanger, and/or a temperature sensor within a tank in which the first heat exchanger is arranged (e.g. within an evaporator tank), in particular at the deepest point within the tank (i.e. the point where the heat exchanging medium is the coldest).
• the control unit may be configured to adjust the speed and/or power of the compressor in dependency of the measured temperature.
• the expansion arrangement is or comprises an electronic expansion device, and wherein the control unit is adapted to adjust the opening state of the electronic expansion device based on an algorithm in dependency of the detected temperature (Tref) and/or pressure.
• Tref detected temperature
• the expansion arrangement is or comprises a thermostatic expansion device, wherein the thermostatic expansion device is configured for adjusting its opening state in dependency of a refrigerant temperature and/or pressure.
• the thermostatic expansion device may comprise a temperature probe/sensor which is in contact with a tube or component of the heat pump to detect the refrigerant temperature (Tref). In reply to the temperature at the probe (sensor) the opening state of the thermostatic expansion device is (self-)adjusted.
• the temperature probe is arranged between the compressor inlet and the outlet of the first heat exchanger or the outlet of the refrigerant flow changing device.
• the temperature probe is arranged at the outlet of the second heat exchanger or at an inlet of the first heat exchanger or within a tank in which the first heat exchanger is arranged (e.g. within an evaporator tank), in particular at the deepest point within the tank (i.e. the point where the heat exchanging medium is the coldest).
• the flow changing device is preferably arranged between the first heat exchanger and the compressor, in particular downstream of the first heat exchanger (in the first operation mode) and upstream of the inlet of the compressor.
• the treatment appliance comprises a cabinet, a heat pump having: a compressor conveying refrigerant through a refrigerant loop, a first heat exchanger, in particular an evaporator, a second heat exchanger, in particular a condenser, an expansion arrangement arranged between the first heat exchanger and the second heat exchanger and being adapted to expand the refrigerant, and a refrigerant flow changing device adapted to change the refrigerant flow direction between a first flow direction and a second flow direction in at least a portion of the heat pump.
• the method comprises: operating the treatment appliance and switching the refrigerant flow changing device to a first operation mode of the heat pump such that the refrigerant is flowing in the first flow direction and to a second operation mode of the heat pump such that the refrigerant is flowing in the second flow direction, wherein in the first operation mode, the second heat exchanger heats a washing liquid and the first heat exchanger cools the heat exchanging medium, and wherein in the second operation mode, the second heat exchanger cools washing liquid and the first heat exchanger heats the heat exchanging medium, and a) directing the refrigerant, in addition to the change of the flow direction, in the first operation mode in a different flow path section of the refrigerant loop than in the second operation mode, and/or b) applying a first control characteristic in the first operation mode and a second control characteristic in the second operation mode, wherein the first and second control characteristics are different from each other, and wherein the first and second control characteristics are applied to one or more of:
• control characteristic for the speed and/or power of the compressor being a variable speed compressor
• control characteristic for controlling the opening state of the expansion arrangement comprising a controllable expansion valve.
• the treatment appliance comprises a tank (e.g. evaporator tank) in which the first heat exchanger is at least partially arranged, in particular an evaporator tank adapted to store the heat exchanging medium and to house and/or being in heat contact with at least a portion of the first heat exchanger.
• the heat exchanging medium is permanently stored in the tank.
• the evaporator tank may have a capacity in the range between 4.0 - 4.5, 4.2 - 4.7, 4.4 - 4.9 or 4.6 - 5.2 liters, preferably 4.7 liters.
• the capacity of the evaporator tank is preferably enough for one main wash phase. E.g. to heat up 4 liter of washing water (tap water) in the tub to 40 °C.
• the evaporator tank comprises an upper region accommodating a first portion of the evaporator and a lower region accommodating a second portion of the evaporator, wherein the first and second portion of the evaporator are arranged at vertically different levels, and wherein the horizontal cross-section area of the lower region is less than the horizontal cross-section area of the upper region.
• a 'region' represents a volume region within the evaporator tank having a vertical extension and being defined between a (fictive) lower and upper horizontal crosssection area within the inner tank space.
• the vertical extension is such that a respective portion of the evaporator is positioned within the volume region.
• the horizontal cross-section area of a (upper/lower/intermediate) region is an average horizontal cross-section area of the respective region, e.g. averaged over all crosssections over the vertical extension of the respective region.
• the lower or upper regions are not regions located within a stub or connector which is connected to the evaporator tank. I.e. the regions are regions conventionally considered to be arranged within the tank volume as such and not within extensions external to the tank volume provided e.g. for peripheral (liquid) connection purposes.
• the volume region of the lower region is arranged below the volume region of the upper region.
• the volume region e.g. the upper and lower horizontal crosssection area
• the volume region may be above each other or at least partially offset to each other.
• the lower region accommodating the second portion of the evaporator and the upper region accommodating the first portion of the evaporator are arranged in volume regions at different vertical height within the tank inner volume, i.e. the volumes of the upper and lower regions have no overlap volume.
• the evaporator tank is external to the tub, in particular the tank is arranged above the tub and/or extends below the top module, more preferably within the top module.
• the evaporator tank is preferably a continuous tank, in particular the lower and upper region of the evaporator tank are connected to each other forming a single tank. Two single tanks that are only fluidly connected to each other are excluded by this definition.
• 'Permanently storing' means that in normal user operation the heat exchanging medium is not exchanged or refreshed.
• the medium may be filled during manufacturing of the machine or when setting the machine to operation at the installation place.
• the medium may be exchanged by maintenance case e.g. by a service person.
• a medium When permanently storing the heat exchanging medium, a medium may be used having a higher heat storing capacity and/or a higher latent heat (enthalpy of fusion) than the washing liquid which basically is water.
• the horizontal cross-section areas decrease in steps from the upper region to the intermediate region and from the intermediate region to the lower region.
• the tank comprises at least two steps, when the tank is seen in vertical cross-section in front view of the washing machine.
• the upper region, the at least one intermediate region and the lower region form a continuous evaporator tank.
• At least one side wall of the tank enclosing the volume of the intermediate region may be a vertical, inclined or rounded side wall.
• the first and/or second portion of the evaporator is formed with pipes, windings of pipes or with microchannels.
• Microchannels have a better heat exchange efficiency, e.g. less volume of tank and/or a shorter evaporator are required for the same amount of heat exchange.
• the pipes may be arranged in the upper and lower region of the evaporator tank horizontally and/or may be arranged inclined extending from the upper region to the lower region of the tank.
• the whole microchannel arrangement is preferably arranged obliquely extending from the upper region to the lower region of the tank, when seen the tank in a vertical cross-section in front view of the washing machine. It is also possible to arrange several microchannel arrangements obliquely, but parallel to each other in the tank.
• At least one microchannel arrangement may be arranged in the upper and lower region, respectively (i.e. the microchannels are arranged horizontally in different heights to each other).
• the lower microchannel arrangement is more compact then the upper microchannel so that the lower microchannel arrangement fits in the lower portion (with smaller horizontal cross-section area) of the evaporator tank.
• the microchannels of the upper and lower region may be arranged above each other or may be at least partially horizontally offset to each other.
• the laundry treatment machine further comprises a top module, wherein when the top module is mounted at the laundry treatment machine it is forming part of the cabinet as a top, and wherein more preferably the top module comprises the evaporator tank and the evaporator.
• 'Module comprises' means that the respective comprised components form part of the top module and are preferably mounted to the top module.
• the top module may comprise a tray element.
• a top wall of the washing machine is preferably mounted on top of the tray element.
• the top module has on its upper side a working top which for example is the top wall in the shape of a plate.
• the components of the top module are pre-assembled such that the top module can be assembled as a whole to the upper side of the laundry treatment machine.
• the evaporator tank together with the evaporator and/or the condenser are arranged at the top of the laundry treatment machine in a pivotable manner.
• a hinge may be provided such that the evaporator tank and/or the condenser can be pivoted at one side (e.g. at the lower end or at a lateral side of the evaporator tank and/or condenser) so that for mounting and/or maintenance purposes (change of the drum driving belt) the tank and/or condenser can be pivoted to the top e.g. after releasing some mounting and/or snap-fit elements supporting the tank and/or condenser at the machine top or housing frame.
• the condenser and/or evaporator tank are provided as a ready-to-be mounted module mounted at the top or top region of the machine cabinet.
• the module is pivotably supported at the machine cabinet or top or cabinet supporting frame.
• the condenser may have an elongate longitudinal extension and one or more of the following may be applicable: (a) the condenser is extending along two sides, along three sides or at least three sides of the evaporator tank, (b) the condenser is guided around the evaporator tank covering an arc around the evaporator tank of at least 70°, at least 80°, at least 100° or at least 120°, and (c) the ratio R between the condenser longitudinal extension L to the condenser maximum or average cross extension Q is at least 10, at least 15 or at least 20.
• the alternatives (a), (b), and/or (c) are the following and are disclosed herein.
• the condenser may be combined with (a), or (b), or (c), or (a) and (b), or (a) and (c), or (b) and (c), or (a) and (b) and (c). In this or an analog way all and/or conjunctions mean this single or multiple combinations.
• 'Longitudinal extension' is the extension when the condenser is straightened to a line and such straightening is 'theoretically' not deteriorating the heat exchanging efficiency of the condenser.
• the 'extending along sides' preferably means that the condenser extends in a horizontal plane around the evaporator, preferably around the upper region of the evaporator tank.
• the 'arc around the condenser' is measured from the geometrical 'center' of the evaporator tank.
• the washing liquid is washing liquid circulated from the interior of the tub through the liquid passage (see below).
• the washing liquid may be water supplied from an external water tap or a mixture of water supplied from the external water tap and a washing agent (e.g. detergent, conditioner, softener and the like).
• At least 80%, 90% or the whole condenser is guided along an outer wall of the evaporator tank - with respect to the length of the condenser which is in heatexchanging contact between the refrigerant passage and the washing liquid passage.
• the condenser may be or may comprise a tube-in-tube arrangement, where a smaller diameter tube is arranged in a larger diameter tube, wherein in particular in the larger diameter tube the refrigerant (or the washing liquid) is flowing around the smaller diameter tube and wherein in the smaller diameter tube the washing liquid (or the refrigerant) is flowing.
• microchannels are arranged in the larger diameter tube, wherein in particular the refrigerant (or the washing liquid) is flowing in microchannels around the smaller diameter tube and wherein in the smaller diameter tube the washing liquid (or the refrigerant) is flowing.
• the refrigerant and the washing liquids are flowing in opposite directions in the heat-connected tubes (counterflow) resulting in higher heat exchanging efficiency (considering here the normal flow direction of the refrigerant when the condenser operates as condenser).
• the condenser may be enclosed by a heat insulating layer, specifically in case of a tube-in-tube arrangement. 'Enclosed' means that essential parts of the condenser are heat insulated.
• the compressor may be mounted in a bottom region of the cabinet or alternatively at the top of the laundry treatment machine, in particular at the top module.
• the compressor may be a variable speed compressor with variable refrigerant flow rate.
• the compressor motor axis When mounted at the top the compressor motor axis is oriented vertical or parallel to the top surface of the laundry treatment machine.
• the compressor motor axis When mounted at the bottom of the cabinet, the compressor motor axis may be in a horizontal plane or may be inclined maximally 15° to the horizontal plane.
• the refrigerant flow changing device comprises a refrigerant inlet and a refrigerant outlet and which is adapted in a first switching state to fluidly connect the refrigerant inlet to a first pipe of the refrigerant circuit and the refrigerant outlet to a second pipe of the refrigerant circuit, and in a second switching state to fluidly connect the refrigerant inlet to the second pipe of the refrigerant circuit and the refrigerant outlet to the first pipe of the refrigerant circuit.
• the refrigerant flow direction may be changed (reverted) by the refrigerant flow changing device (preferably a four-way valve) outside the compressor.
• the refrigerant flow changing device is a four-way-valve comprising a sliding element that may be actuated by a refrigerant pressure difference at two ends of the valve between which the sliding element can move.
• the sliding element may be adapted to switch in the first switching state in which the refrigerant flows in the first flow direction in the first operation mode and in the second switching state in which the refrigerant flows in the second flow direction in the second operation mode.
• the laundry treatment machine further comprises a washing liquid circulation unit which is adapted to circulate the washing liquid from the tub through the condenser and back to the tub.
• the circulation unit may comprise a circulation pump (jet pump), a suction line connecting the tub to the inlet of the circulation pump and a return line connecting the outlet of the pump to the tub or to a fluid passage which is connected to the tub.
• the inlet of the suction line may be connected to a sump of the tub.
• the outlet of the return line may be connected (a) to a spray nozzle that may be arranged at the tub or at a loading opening of the tub.
• the spray nozzle may be adapted to spray the circulated washing water towards the drum interior.
• the spray nozzle may be a shaped pipe where in particular the circulated liquid is released without water pressure.
• the liquid exiting for example a nozzle may be pressurized (having e.g. a predefined directivity) or may be pressure-free.
• the spray nozzle introducing water into the tub is designed to change the shape of the liquid jet, e.g. by enlarging it as a sort of 'V or expanded spray.
• the outlet of the return line is connected (b) to the interior of a detergent drawer housing of the laundry treatment machine from where the circulated washing water may be guided back to drum interior.
• the outlet of the return line is connected (c) to a manifold of the laundry treatment machine which may be fluidly connected to the interior of the tub or the outlet of the return line is connected first to the drawer housing and then to the manifold.
• a portion of the return line forms the liquid passage of the condenser.
• the laundry treatment machine may be a washing machine or a washer-dryer having the first operation mode of the heat pump in which during at least a portion of a washing cycle the circulated washing liquid is heated, and/or having the second operation mode of the heat pump in which during at least a portion of a washing cycle the circulated (washing) liquid is cooled.
• the washing liquid is used for de-icing the evaporator in e.g. the last washing cycle and/or during at least one rinsing phase.
• the top module comprises a tray element which provides a supporting structure of the top module, wherein the evaporator tank is integrated in the tray element.
• the tray element has one, two, three or four peripheral outer sides (side walls) that preferably extend downward from an upper plane of the tray element and/or form lateral side surfaces of the tray element.
• the condenser is guided along the lateral outer wall of the evaporator tank along at least two sides of the evaporator tank and/or along an arc of at least 180° around the evaporator tank, and wherein the condenser is at least partially received in or at a receptacle along the path around the evaporator tank.
• the condenser is guided along the peripheral outer sides of the tray element, namely along two, three or four peripheral outer sides.
• the condenser is arranged within the footprint (when seen from above in operational orientation) of the tray element.
• the tray element has lateral outer side walls at two, three or four sides and optionally the condenser is arranged at a vertical level to be located behind the sides of the tray level (when seen in side view).
• the outer lateral wall of the evaporator tank forms part of the receptacle for the condenser.
• the evaporator tank may be part of the receptacle and may stabilize/support the condenser.
• the receptacle is only formed by lateral walls of the tray element.
• the outer peripheral walls (see above) of the tray element form part of the receptacle for the condenser.
• the condenser is received between the outer peripheral wall of the tray element and the outer lateral wall of the evaporator tank.
• the flow changing device is mounted at or on the tray element, wherein the flow changing device is adapted to switch the refrigerant flow in the heat pump circuit between the normal operation mode of the heat pump (i.e. forward refrigerant flow direction) and the reverse operation mode of the heat pump (i.e. reversed/inverted refrigerant flow direction).
• the normal operation mode of the heat pump i.e. forward refrigerant flow direction
• the reverse operation mode of the heat pump i.e. reversed/inverted refrigerant flow direction
• the tray element has lateral outer walls on at least three sides thereof. This increases stability of the tray element and top module.
• the outer lateral walls of tray element preferably form outer lateral/peripheral walls of top module.
• the outer lateral walls of tray element may form part of the receptacle for receiving the condenser.
• the receptacle (recess) has the shape or substantially the shape of the condenser when mounted at the top module.
• the outer lateral walls laterally protect condenser also during assembling process. More preferably the receptacle is formed by the outer lateral walls of the tray element and the outer walls of the evaporator tank.
• the evaporator, the condenser, the expansion device and all the refrigerant pipe connections are mounted in or on the top module, preferably in or on the tray element.
• the compressor may be mounted in or on the top module and/or tray element.
• the laundry treatment machine further comprises a heater arranged within the tub for heating the washing liquid.
• the heater may be used for alternatively heating the washing liquid if the heat pump system does not work or for supporting the heat pump.
• the heater is used if the desired temperature of the washing liquid is higher than can be achieved by only using the heat pump system for heating the washing liquid. E.g. if the desired temperature of the washing liquid is higher than 60, 65, 70 or 75 °C, then the heater is used. E.g. to heat up the washing liquid pre-heated by the condenser of the heat pump to the predetermined temperature being higher than the maximum condenser heating temperature.
• the machine further comprises an external evaporator, in particular an airheated evaporator, arranged at an inlet of the compressor for heating the refrigerant of the heat pump.
• the inlet refers to the refrigerant inlet at the compressor in the normal operation mode of the heat pump.
• the external evaporator is an air-heated evaporator in which ambient air is used for heating the refrigerant.
• the refrigerant flow changing device changes from the first operation mode of the heat pump to the second operation mode of the heat pump, the role of the evaporator and the condenser is reversed, but the external evaporator preferably remains working as an evaporator.
• the operation of the external evaporator is preferably independent of the operation mode of the heat pump.
• Each individual feature of the articles treatment appliance e.g. laundry treatment machine
• any sub-group of features e.g. any of the dependent claims
• any individual (functional) feature or sub-group of (functional) features of the method can be combined with the articles treatment appliance (e.g. laundry treatment machine) as a functional feature of the machine.
• Fig. 1 a perspective view of another washing machine with a top module
• FIG. 2 an exploded view of the washing machine of Fig. 1 without the front and top wall
• Fig. 3 a detailed perspective view of the pump arrangement of Fig. 1,
• Fig. 4 a front view of the upper portion of the washing machine of Fig. 1 without the front wall
• Fig. 5 an exploded view of the top module and the compressor of Fig. 2,
• Fig. 6 an exploded view of the top module and the compressor of Fig. 2 in another perspective view
• Fig. 7 a perspective view of the top module and the evaporator of Fig. 2 with partial section of the tray element
• Fig. 8 a perspective view of the washing machine of Fig. 1 without the front and top wall and with another configuration of the circulation pump,
• Fig. 9 a detailed perspective view of the pump arrangement of Fig. 8,
• Fig. 10 a front view of the washing machine of Fig. 8,
• Fig. 11 a schematic diagram of the heating and cooling process during circulation of the washing liquid in a washing machine
• Fig. 12 a schematic diagram showing a refrigerant circuit
• Fig. 13 a schematic diagram showing another refrigerant circuit
• Fig. 14 a schematic diagram showing another refrigerant circuit
• Fig. 15 a schematic diagram showing of another refrigerant circuit
• Fig. 16 a schematic diagram showing another refrigerant circuit
• Fig. 17 a schematic diagram showing another refrigerant circuit
• Fig. 18A a schematic diagram showing the coefficient of performance (COP) of the heat pump system during a washing cycle
• Fig. 18B a schematic diagram showing the energy consumption of the heat pump system during the washing cycle of Fig. 18A
• Fig. 19 a schematic diagram showing a configuration of a refrigerant flow changing device in the first operation mode
• Fig. 20 a schematic diagram showing the refrigerant flow changing device of Fig. 19 in the second operation mode
• Fig. 21 a schematic diagram showing another configuration of the refrigerant flow changing device in the first operation mode
• Fig. 22 a schematic diagram showing the refrigerant flow changing device of Fig. 21 in the second operation mode
• Fig. 23 a schematic diagram of the heating and cooling process during circulation of the washing liquid in a dishwasher.
• Fig. 1 is a perspective view of the outer appearance of an articles treatment appliance, in this case a washing machine 2 with a top module 5.
• the washing machine 2 has a cabinet 4 comprising two side walls 10, a front wall 8, a bottom (plate or shell) 56 (see: Fig. 2) and a rear wall 24 (see also: Fig. 2).
• the top may be formed by the top module 5 which may be mounted on the cabinet 4 by fastener elements, e.g. by screws or snap-in elements.
• a top wall 9 may be arranged on top of the washing machine 2, in particular on top of the top module 5 and is preferably forming a work top. It should be clear to the skilled person that all the structural features and different configurations of the first and second operation modes described above and below are also applicable to the washing cycle of a domestic laundry or dishes treatment machine, more preferably a washer dryer, or a dishwasher.
• the upper region of the machine front face comprises a detergent drawer 12 with a handle 13 which is preferably arranged at the left side of the upper region.
• the detergent drawer 12 is used for storing and in particular for providing washing agents (e.g. detergent, softener, conditioner, auto dosing or other treatment agents) during washing cycles.
• the washing machine 2 further has a control panel 14 preferably arranged at the middle and/or right side of the upper region of the machine front face.
• the control panel 14 preferably comprises a display for displaying information about the washing program (e.g. energy consumption, duration of the washing cycle and the like) and an input device.
• the input device is a control knob provided for selecting between different washing programs.
• the knob is preferably arranged between the control panel 14 and the detergent drawer 12.
• the front wall 8 may comprise an air inlet opening (not shown) which may be arranged near the center.
• a cover for service opening 22a may be provided at the front wall 8 e.g. on the right side of the lower region of the front wall 8.
• the air inlet opening enables air entering the interior of the washing machine 2.
• the air passing through the inlet opening may be provided for cooling the compressor and further electronic components inside the washing machine 2 with air.
• the washing machine 2 shown in Fig. 1 is a front- loading machine having preferably a horizontal drum rotation axis, but in alternative embodiments the drum may be inclined relative to the horizontal and vertical directions.
• Fig. 2 is an exploded view of the washing machine of Fig. 1 without the front and top wall 8, 9.
• Fig. 3 is a detailed perspective view of the pump arrangement of Fig. 2 and
• Fig. 4 is a front view of the upper portion of the washing machine of Fig. 2 without the front wall.
• a tub 58 and a drum 60 rotatably arranged in the tub 58 and in which laundry is received, are arranged inside the cabinet 4.
• the tub 58 may be suspended by spring dampers 30 and/or a balance weight 28 may be provided for stabilizing the tub 58 and the drum 60 (see Fig. 4).
• a bellow 62 may be mounted to the tub 58 or to the tub 58 and to the front wall 8 (not shown).
• a detergent drawer housing 12a for receiving the drawer 12 is arranged in the upper region of the washing machine 2.
• the detergent drawer housing 12a is preferably arranged on the left side of the upper region of the washing machine 2, in particular below the top module 5.
• the detergent drawer 12 is inserted into the detergent drawer housing 12a.
• a water supply unit (not shown) connected to the detergent drawer housing 12a may provide fresh water from the outside of the washing machine 2 to flush the detergent from the detergent drawer 12 through the water supply and the water inlet 65 into the tub 58.
• a drum drive arrangement may comprise a motor for driving the drum 60 and optionally a torque transmission element (e.g. a belt) connecting the motor and the drum 60 for driving the drum 60.
• the motor may be arranged at the rotation axis of the drum 60 (direct drive arrangement) or may be arranged under the rear region of the tub 58.
• the drum drive arrangement is applicable for all embodiments of washing machines disclosed herein.
• the washing liquid supplied to a tub 58 of the washing machine 2 is circulated by and through a washing liquid circulation unit 64 to save water and energy.
• the washing liquid circulation unit 64 the washing liquid is guided through a first, second, third and fourth water circulation sections 64a, 64b, 64c, 64d.
• the first water circulation section 64a connects the tub outlet (not shown, e.g. at the sump of the tub 58) to a circulation pump 66.
• the circulation pump 66 is preferably arranged in the bottom region, e.g. at the lower right comer at the front of the washing machine 2.
• the second water circulation section 64b extends between an outlet of the circulation pump 66 and a washing liquid condenser inlet 82
• the third water circulation section 64c extends between the washing liquid condenser inlet 82 and a washing liquid condenser outlet 84 (within the condenser inner tube)
• the fourth water circulation section 64d connects the washing liquid condenser outlet 84 to the tub 58 via a nozzle 65.
• at least a portion of the second water circulation section 64b may extend along a side wall or a corner of the washing machine 2, e.g. at the left side of the washing machine 2 parallel to the side wall 10.
• a condenser 81 comprises the washing liquid condenser inlet 82 and outlet 84 and a refrigerant condenser inlet 86 and outlet 88.
• the condenser 81 is used for heating the washing liquid within the washing liquid circulation unit 64.
• the washing liquid is circulated in the washing liquid circulation unit 64 through the water circulation sections during a washing cycle and is heated by the heated refrigerant when passing the condenser 81.
• the condenser 81 may be a tube-in-tube condenser consisting of an inner tube for guiding the washing liquid, an outer tube for guiding the refrigerant and an outer insulation layer when starting from the inside of the condenser 81.
• connection element comprising the refrigerant outlet 88 is provided at the water inlet portion of the condenser 81 and which is adapted to guide refrigerant through the outer tube. More preferably, an inner surface of a first end portion of the connection element is connected to the outer surface of the inner tube of the condenser and an inner surface of a second portion of the connection element is connected to the outer surface of the outer tube of the condenser.
• the washing liquid may flow in the outer tube of the condenser and the refrigerant may flow in the inner tube of the condenser.
• the circulation pump 66 is preferably arranged in the bottom region of the washing machine 2, e.g. in the lower left corner at the front of the washing machine 2.
• the circulation pump 66 is used to suck in washing liquid (during a washing phase) or water (during a rinsing phase) from the sump of the tub 58, in particular from the drain manifold which is arranged at the lower part of the sump 140 and to recirculate the liquid to the upper part of the tub 58 where the liquid is introduced into the tub 58 by the water inlet (e.g. nozzle) 65.
• the washing machine 2 further comprises a drain pump 72.
• the drain pump 72 which is connected to a tub outlet (e.g. via the sump, in particular from the drain manifold which is arranged at the lower part of the sump 140) may be connected to a water drain 70 which is used for draining the washing liquid at the end of a washing cycle out of the washing machine 2.
• 'washing liquid' comprises water with resolved treatment agent, water used e.g. for rinsing and other liquids used during a washing, laundry treatment and/or drying cycle.
• the drain pump 72 is preferably arranged in the bottom region of the washing machine, e.g. in the lower right corner at the front of the washing machine 2. As shown in Figs.
• the washing machine 2 may have a mixing pump 76 which may be connected to the tub outlet, and which sucks in water and detergent from the bottom of the tub (e.g. the sump of the tub 58, in particular from the drain manifold which is arranged at the lower part of the sump) at the beginning of a washing cycle after detergent has been introduced into the tub 58 and re-send the water and detergent to the tub 58, e.g. to the sump of the tub or in particular to the tub 58 below a water heater (not shown), by a return line 77.
• the mixing pump 76 is preferably arranged in the bottom region of the washing machine, e.g.
• the drain pump 72, the circulation pump 66 and the mixing pump 76 are integrated in a pump group.
• a filter of a filter opening 68 is provided upstream of the mixing and drain circuit.
• the heat pump comprises a compressor 36, a first heat exchanger (e.g. an evaporator) 102 and a second heat exchanger (e.g. a condenser) 81 which are preferably arranged at the inside of the washing machine 2.
• the compressor 36 is preferably arranged in the bottom region, e.g. at the lower left corner at the front of the washing machine 2.
• the compressor 36 is mounted on at least one damping element 92.
• a refrigerant circulation circuit 42 comprises a first, second, third, fourth, fifth and sixth refrigerant circuit section.
• the first refrigerant circuit section 44D extends between the refrigerant condenser outlet 88 and the evaporator inlet 104, the second refrigerant circuit section 46D between the evaporator outlet 106 and the first inlet of the switching valve 78 (refrigerant flow changing device), the third refrigerant circuit section 48D between the first outlet of the switching valve 78 and the compressor inlet 110, the fourth refrigerant circuit section 50D between the compressor outlet 112 (see Fig.
• the first refrigerant circuit section 44D may comprise an expansion arrangement 40 (e.g. a capillary as shown in Fig. 5) for controlling the amount of refrigerant released into the evaporator 102.
• the switching valve 78 may be arranged below the condenser 81, preferably between a drawer housing 12a and the rear wall 24 of the washing machine 2. Most preferably, the longitudinal axis of the switching valve 78 extends vertically (in an operational position of the washing machine (see Fig. 2).
• a refrigerant flow direction 94 in the first switching state of valve 78 (details below) and a washing liquid flow direction 96 within the condenser 81 are indicated by arrows in some of the following Figures (see: Figs. 5 and 16).
• the dashed arrow indicates the washing liquid flow direction 96 and the filled arrow indicates the refrigerant flow direction 96.
• the top module 5 may comprise a tray element 6 which is mounted on the top of the washing machine 2, and which is preferably mechanically connected to the two side walls 10, the front wall 8 and/or the rear wall 24 of the washing machine 2.
• the tray element 6 preferably has lateral side walls 7 along the periphery of the tray element and/or downward from an upper plane/plate of the tray element.
• the top module 5 comprises the condenser 81 and the evaporator 102.
• the tray element 6 comprises an evaporator tank 100 which may be arranged on only one side of the entire tray element 6.
• the evaporator tank 100 comprises the evaporator 102 and may form with an evaporator tank cover 32 a closed tank for permanently storing a heat exchanging medium.
• the evaporator 102 is surrounded by (immersed in) the heat exchanging medium stored in the evaporator tank 100 for exchanging heat between the refrigerant flowing through the evaporator 102 and the heat exchanging medium.
• the evaporator inlet 104 and outlet 106 may be arranged at the bottom of the evaporator tank 100, e.g. near the front wall 8 of the washing machine 2.
• the tank 100 is arranged on the right side of the tray element 6 when seen the washing machine in front view.
• the switching valve 78 may be arranged between the top module 5 and the drawer housing 12a.
• the switching valve 78 and/or at least portions of the refrigerant circuit sections may be arranged in the remaining portion of the tray element 6, next to the evaporator tank 100.
• the switching valve 78 is arranged vertically, more preferably the longitudinal axis of valve 78 is parallel to the front/rear wall of the washing machine 2.
• the tray element 6 may further comprise a maintenance opening 128, preferably with a rectangular shape, arranged above the switching valve and/or the refrigerant circuit sections.
• the evaporator tank 100 and the tray element 6 are formed in a single piece, for example by injection molding of plastic or by deep drawing of a metal sheet.
• the evaporator tank 100 is preferably covered by the evaporator tank cover 32.
• a gasket is arranged between the evaporator tank cover 32 and the evaporator tank 100.
• the evaporator tank cover 32 may be mounted to the evaporator tank 100 or the tray element 6 detachable e.g. by screws or non-detachable e.g. by welding or gluing.
• the evaporator tank cover 32 may comprise seats and/or ribs 34 at the outer side for receiving a thermo-insulating material.
• the evaporator inlet and/or outlet 104, 106 may be arranged on a side wall of the evaporator tank 100, preferably on the rear side wall when looking to the washing machine in front view.
• the evaporator inlet and/or outlet 104, 106 may be arranged at the bottom of the evaporator tank 100.
• the evaporator tank 100 may comprise mounting elements 108 and/or the side facing the evaporator tank 100 of an evaporator tank cover 32 may comprise fixing elements 138, each for fixing the evaporator 102 when arranged within the tank 100.
• the third and fourth refrigerant circuit section 48D, 50D which preferably extend between the top and the bottom of the washing machine 2 are preferably flexible pipes.
• the piping of the remaining refrigerant circuit sections 44D, 46D, 52D - except the piping of the heat exchanger(s) itself - may also be provided as flexible pipes.
• the flexible pipes may be easily adapted to paths which are not straight without requiring mechanical bending.
• a large part of the third and fourth refrigerant circuit sections 48D, 50D may extend between the bottom region and the top region of the washing machine 2 where the top module 5 is arranged.
• the third and fourth circuit sections 48D, 50D may run along at the left side of the washing machine 2 from bottom to top parallel to the side wall 10 (see: Fig. 2).
• the switching valve 78 may be arranged next to the evaporator tank 100 for receiving a heat exchanging medium (e.g. water), preferably on the left side of the evaporator tank 100 when seen the washing machine 2 in a front view.
• a heat exchanging medium e.g. water
• the valve 78 may be arranged in a horizontal, but preferably vertical position as shown in Fig. 2.
• Fig. 7 shows a perspective view of the top module and the evaporator of Fig. 2 with partial section of the tray element 6.
• the tray element 6 may comprise a recess provided on an underside of the tray element 6 (a surface of the tray element 6 facing the tub 58 of the washing machine when mounted) that may form a channel extending along at least one side of the evaporator tank 100.
• the channel preferably has the shape of the condenser 81, for receiving the condenser 81 when mounted on top of the washing machine 2.
• the condenser 81 is guided at least partially around the evaporator 102, preferably extending along one side, two sides, three sides or four sides of the evaporator tank 100.
• the condenser 81 is guided along the inner side of peripheral side walls 7 of the tray element.
• the side walls 7 form part of a receptacle for receiving the condenser 81 thereby protecting and/or supporting the condenser within the tray element (top module) during assembling.
• the condenser is arranged at a vertical level (in operational orientation) between the evaporator tank and the peripheral side walls 7 - at least along sides of evaporator tank where no further components of the tray element are arranged.
• the condenser 81 is positioned between the peripheral side walls 7 and the outer lateral wall of the evaporator tank 100 at one, two or three sides of the evaporator tank.
• Fig. 8 is a perspective view of the washing machine of Fig. 1 without the front and top wall and with another configuration of the circulation pump.
• Fig. 9 is a detailed perspective view of the pump arrangement of Fig. 8
• Fig. 10 is a front view of the washing machine of Fig. 8.
• the basic design of the washing machine of Figs. 8 to 10 may be identical to the washing machine of Fig. 2. Therefore, only the differences between both washing machines 2 are outlined in the following. Otherwise, the elements and functions as described above with respect to the other elements of the washing machine of Fig. 2 correspondingly also apply individually, in subgroups or as a functional group to the embodiment of Figs. 8 to 10.
• the circulation pump (jet pump) 66 may be arranged below the tub 58, in particular the circulation pump 66 is fixed to the tub 58 from below (difference to the circulation pump of Fig. 2 which is arranged at the bottom right comer of the washing machine).
• a first water circulation section 64a* connects the tub outlet to the circulation pump 66.
• a first portion of the first water circulation section 64a* is connected to the filter opening 68 and a second portion of the first water circulation section 64a* connects the filter opening 68 with the circulation pump 66 (see: Fig. 9).
• a second water circulation section 64b* connects the circulation pump outlet with the washing liquid condenser inlet (not shown, cf. Fig. 2).
• T1 Fig. 11 is a schematic diagram of the functional elements used for heating and cooling the washing liquid during circulation of the washing liquid in the washing machines described above.
• the washing liquid is circulated in the washing liquid circulation unit 64 and the refrigerant is circulated in the refrigerant circulation circuit 42.
• the washing liquid flow direction 96 and the refrigerant flow directions 94 are indicated by arrows.
• the first water circulation section 64a connects a tub outlet 74 to the inlet of the circulation pump 66.
• the washing liquid is directed to the condenser 81 via the second water circulation section 64b.
• the washing liquid flows within the condenser 81 through the third water circulation section 64c.
• the first operation mode comprising the heating of the washing liquid used e.g. during a washing phase of a washing cycle and second the cooling of the washing liquid and thus the heating of the heat exchanging medium 101 within the evaporator tank used e.g. for de-icing the evaporator (herein called second operation mode), in particular during a rinsing (e.g. the last rinsing phase) of a washing cycle.
• the heating of the washing liquid is stopped for example if the heat transfer to the washing liquid is no longer required or possible (e.g. no circulation, washing liquid maximally heated and/or heat exchanging medium maximally depleted of heat (frozen)).
• Heat e.g. residual heat of the heat pump
• the refrigerant In the first operation mode (heating mode), within the refrigerant circulation circuit 42, starting from the refrigerant condenser outlet 88, the refrigerant is directed by the first refrigerant circuit section 44D through the expansion device 40 to the evaporator 102 (i.e. section 44D comprises the expansion device 40).
• the compressor 36 arranged within the refrigerant circulation circuit 42 creates a vacuum applied to the evaporator 102.
• the heat exchanging medium in the evaporator tank 100 is in heat-exchanging contact with the evaporator 102. The medium is cooled down and finally changes from the liquid to the solid phase for releasing heat. The heat released heats the refrigerant in the evaporator 102 which then evaporates.
• the heated refrigerant as a gas phase is sucked by the compressor 36 through the second refrigerant circuit section 46D, the switching valve 78 and the third refrigerant circuit section 48D.
• the compressed refrigerant is passed through the fourth refrigerant circuit section 50D, the switching valve 78 and fifth refrigerant circuit section 52D to the condenser 81 through the refrigerant condenser inlet 86.
• the refrigerant normal flow direction 96
• the washing liquid flow in opposite directions for an improved heat exchange.
• the washing liquid is heated by transferring the heat from the refrigerant to the washing liquid.
• the refrigerant cools down and from the washing liquid condenser inlet 82 to the washing liquid condenser outlet 84, the washing liquid is heated.
• the heated washing liquid exits the condenser 81 through the washing liquid condenser outlet 84 and the further flow path of the washing liquid may optionally be selected by a first flow diverter 144a.
• the first flow diverter 144a may in a first state selectively direct the washing liquid to the tub 58 through the water inlet 65 or in a second state selectively to the drawer housing 12a.
• the circulated washing liquid may also be passed from the condenser outlet 84 to the drawer housing 12a.
• the washing liquid flows into a manifold 146 which may optionally comprise a second flow diverter 144b (instead or in addition to the first flow diverter 144a).
• the second flow diverter 144b may selectively direct the washing liquid through the fourth water circulation section 64d and the water inlet 65 to the tub 58.
• the washing liquid flows through the sump 140 out of the tub and is circulated again as described above.
• the washing liquid which exits the tub 58 through the sump 140 is drained by the drain pump 72 through the water drain 70.
• the second operation mode (cooling/regeneration mode) is used for de-icing the evaporator at the end of a washing cycle or during one or more rinsing phases.
• the refrigerant flow direction is reverted as indicated by the white filled arrows in Fig. 57 (the black filled arrows indicate the normal flow direction 96 for the heating process of the washing liquid).
• the reversal of the refrigerant flow through the condenser 81, expansion device 40 and evaporator 102 is provided by a refrigerant flow changing device 78.
• the evaporator 102 works as a condenser and heats the heat exchanging medium within the evaporator tank 100.
• the condenser 81 operates as an evaporator and cools the circulated liquid (which is preferably freshly supplied tap water and/or water from the previous rinsing).
• the expansion device 40 preferably is a dual-direction expansion device, e.g. a capillary that operates independent of the flow direction. Alternatives for the capillary tube are described below.
• the cooled washing liquid exiting the condenser 81 may be directed through the first flow diverter 144a to the drawer housing 12a in the fourth water circulation section 64d. Then the washing liquid may flow to the second flow diverter 144b in the manifold 146 and from there to the water inlet 65. From the water inlet 65 the liquid may flow into the tub 58 and then to the tub sump 140.
• all or enough heat is extracted from the washing liquid and/or when the heat exchanging medium in the evaporator 102 is sufficiently heated (e.g.
• the cooled-down washing liquid can be drained with the drain pump 72 which is connected to the sump 140, in particular to the drain manifold of the sump 140, through the water drain 70.
• the flow changing device 78 has two switching states, wherein the refrigerant conveyance direction of the compressor 36 is not changed in both switching states. a) In a first state (first operation mode of the heat pump, heating mode as described above) the evaporator 102 operates as evaporator and the condenser 81 operates as condenser. The refrigerant compressed by the compressor and coming from the compressor outlet is directed by the switching valve 78 to the condenser 81. The refrigerant from the evaporator 102 is sucked in through the switching valve 78 to the compressor inlet.
• a second state (second operation mode of the heat pump (regeneration mode) in which the heat pump is operated in a reverse operation mode) the refrigerant compressed by the compressor is directed by the switching valve 78 to the evaporator 102.
• the refrigerant exiting the condenser is sucked in by the compressor 36 through the switching valve 78 being in its second switching state.
• the evaporator 102 operates as a condenser and the condenser 81 operates as an evaporator.
• the heat exchanging medium within the evaporator tank 100 is heated by the evaporator 102 working as a condenser.
• ice formed within the evaporator tank can be melt by the second operation mode.
• an external evaporator 148 in particular an air heated evaporator, may be provided at the inlet of the compressor 36.
• the external evaporator 148 is provided between the flow changing device 78 and the inlet of the compressor 36. Refrigerant exiting the flow changing device 78 may be guided through the external evaporator 148 and then to the inlet of the compressor 36.
• the external evaporator 148 further heats the refrigerant and thus the washing liquid within the condenser 81 in the first operation mode of the heat pump and heats the heat exchanging medium within the evaporator tank 100 in the second operation mode of the heat pump.
• an air flow A i.e.
• the "cooled" air exiting the evaporator is guided along the compressor 36 before being guided out of the washing machine 2 such that the compressor 36 is cooled by the air flow A. Therefore, warm air and not cold air is blown into the environment surrounding the washing machine 2 and thereby it may be prevented that operation of the evaporator 148 results in cooling of the environment. This could be inconvenient for the user especially on cold days.
• a heater 142 may be arranged inside the tub 58, preferably at the bottom of the tub 58 (e.g. the sump of the tub), for heating the washing liquid.
• the washing liquid may be additionally heated by the heater, preferably after heating the washing liquid in the first operation mode and when maximum liquid temperature and/or minimum heat exchanging medium temperature has reached, to further increase the washing liquid temperature, e.g. to 60, 70 or 80°C if provided by the washing program. If the heat pump system is defect, the washing machine may also be operated normally by using the heater 142 for heating the washing liquid.
• Fig. 11 The functional arrangement shown in Fig. 11 is applicable to all above embodiments of a laundry treatment machine. In particular applicable in all embodiments of a washing machine which are disclosed herein in more detail. Although not shown in the detailed embodiments above, for example the first and/or second flow diverter 144a, 144b may be provided.
• the refrigerant flow direction 94a in the first operation mode is indicated by dashed arrows and the refrigerant flow direction 94b in the second operation mode is indicated by solid arrows.
• the refrigerant circuits and arrangements are likewise applicable in dishwashers and articles treatment appliances using a washing liquid in general.
• the compressor 36 of each refrigerant circuit may be a fixed speed compressor or may be a variable speed compressor (VSC).
• the expansion arrangements 40 may comprise one or more expansion devices (expansion valve).
• each expansion device 40 may be a fixed expansion device (i.e. refrigerant flow rate through device can not be adjusted) such as a capillary or a bi-directional expansion device, or may be a controllable expansion device (i.e. the refrigerant flow rate through device is controllable) such as a thermostatic expansion device, or an electric expansion device.
• each filter 158 may be a mono-directional or bi-directional filter.
• Fig. 12 is a schematic diagram of a refrigerant circuit. In contrast to the refrigerant circuit shown in Fig. 11, the section between the evaporator 102 and the condenser 81 is different in Fig. 12.
• the refrigerant is directed from the evaporator 102 along a first refrigerant flow path section 160, 162a to the condenser 81, and in the second operation mode, the refrigerant is directed from the condenser 81 along a second refrigerant flow path section 160, 162b to the evaporator 102.
• each of the first and second flow path sections 160, 162a, 162b comprises non-shared refrigerant flow path sections 162a, 162b (i.e. the refrigerant flows through the first non-shared refrigerant flow path section 162a only in the first operation mode, and through the second non-shared refrigerant flow path section 162b only in the second operation mode) and a common (shared) refrigerant flow path section 160.
• the expansion arrangement 40 and a filter arrangement 158 (comprising at least one filter) arranged upstream of the expansion arrangement 40 are arranged in the common flow path section 160.
• the expansion arrangement 40 comprises a controllable expansion device, in particular an electronic expansion device.
• the expansion arrangement may be a non-controllable or fixed expansion device like a capillary tube.
• Flow rectifier means 156 such as check valves/one-way valves may be provided in the first and second refrigerant flow path sections 160, 162a, 162b of Fig. 12 (and Figs. 13 and 17) for passing the refrigerant through either the first flow path section 160, 162a in the first operation mode or through the second flow path section 160, 162b in the second operation mode.
• the check valves 156 are shown in Fig. 12 (and also in Figs. 13 to 17) as triangles, wherein the refrigerant can only pass through the check valves in one direction, namely in the direction of the tip of the triangles.
• the treatment machine may comprise a control unit 150 adapted to operate the treatment appliance and to switch the refrigerant flow changing device 78 to the first operation mode of the heat pump such that the refrigerant is flowing in the first flow direction and to the second operation mode of the heat pump such that the refrigerant is flowing in the second flow direction.
• the appliance may comprise a temperature sensor 152 and/or a pressure sensor 154, wherein one or both sensors are preferably arranged between the inlet of the compressor 36 and the refrigerant flow changing device 78.
• the control unit 150 may be adapted to receive temperature and/or pressure signals from the sensors 152, 154 and to adjust the opening state of the electronic expansion device based on an algorithm in dependency of the detected temperature (Tref) and/or pressure.
• the expansion device 40 may be a thermostatic expansion device, wherein the thermostatic expansion device is adapted to adjust its opening state in dependency of the refrigerant temperature and/or pressure measured by the sensors 152, 154 (i.e. in this case the control unit 150 is not necessary for controlling the expansion device since the thermostatic expansion device is directly adjusted by the measured temperature/pressure of the refrigerant).
• controllable expansion device Due to the controllable expansion device, it is possible to adjust the refrigerant flow through the device and thus to adjust the pressures and/or temperature of the heat pump system as required in each of the first and second operation modes. Therefore, the efficiency of the system can be improved.
• Fig. 13 is a schematic diagram of another refrigerant circuit which is similar to Fig. 12.
• the filter arrangement 158 is not arranged in the common flow path section 160, but the filter arrangement 158 comprises a first filter 158a arranged in the first non-shared flow path section 162a and a second filter 158b arranged in the second non-shared flow path section 162b.
• each filter 158a, 158b is arranged upstream of the expansion arrangement. I.e. in this example, in the first operation mode, the refrigerant flows from the evaporator 102 through the first filter 158a, then through the expansion arrangement 40 arranged in the common flow path 160 and then to the condenser 81.
• the refrigerant flows from the condenser 81 (working as evaporator) through the second filter 158b, then through the expansion arrangement 40 arranged in the common flow path 160 and then to the evaporator 102.
• the flow direction in the common flow path 160 is the same in both operation modes.
• the compressor 36, the flow changing device, the respective refrigerant flow path sections, and the control unit 150 and the sensors 152, 154 (for adjusting a controllable expansion device) shown in Figs. 12 and 13 are omitted, but are equally applicable.
• the expansion arrangement 40 and the filter arrangement 158 are arranged, wherein the filter arrangement 158 is arranged upstream of the expansion arrangement 40, respectively.
• a first expansion arrangement (device) 40a and in the second non-shared refrigerant flow section 162b a second expansion arrangement (device) 40b is arranged.
• the refrigerant flows from the evaporator 102 through the filter arrangement 158 and the expansion arrangement 40 arranged in the first nonshared refrigerant flow section 162a and then to the condenser 81.
• the refrigerant flows from the condenser 81 (working as evaporator) through the filter arrangement 158 and the expansion arrangement 40 arranged in the second non-shared refrigerant flow section 162b and then to the evaporator 102.
• the refrigerant flows in the first and second operation modes through different filter arrangements and expansion arrangements. Therefore, it is possible to provide an expansion arrangement which is adapted to provide pressures and/or temperature in the heat pump system as required in each of the first and second operation modes.
• the refrigerant is directed between the evaporator 102 and the condenser 81 in both operation modes along the same common refrigerant flow path section 160 in opposite directions.
• the expansion arrangement 40 arranged in the common flow path 160 is therefore a bi-directional expansion device, i.e. the refrigerant can flow through the expansion device in both directions.
• the filter arrangement 158 comprises at least one filter arranged upstream and at least one filter arranged downstream of the expansion device.
• the filters are bi-directional filters enabling refrigerant flow in both directions.
• the bi-directional filter preferably has internally different flow paths for the first and second operation mode. Thus, debris and impurities collected within the filter in the first operation mode is prevented from being washed out, when the refrigerant flows through the bi-directional filter in an opposite direction in the second operation mode.
• the refrigerant in the first operation mode, is directed from the evaporator 102 along the first non-shared refrigerant flow path section 162a, a common flow path section 160 and another first non-shared refrigerant flow path section 162a to the condenser 81.
• the filter arrangement 158 in the first non-shared refrigerant flow path section 162a at the evaporator 102 (i.e. directly connected to the evaporator 102) the filter arrangement 158 is arranged and in the first non-shared refrigerant flow path section 162a at the condenser 81 (i.e. directly connected to the condenser 81) the first expansion arrangement 40a is arranged.
• the refrigerant is directed from the condenser 81 along the second non-shared refrigerant flow path section 162b, a common flow path section 160 and another second non-shared refrigerant flow path section 162b to the evaporator 102.
• the second expansion arrangement 40b is arranged and in the first non-shared refrigerant flow path section 162b at the condenser 81 (i.e. directly connected to the condenser 81) the filter arrangement 158 is arranged.
• the refrigerant direction in the common flow path 160 is opposite in both operation modes.
• the refrigerant circuit of Fig. 17 is similar to the circuit of Fig. 16. Instead of the two expansion arrangements 40 in each of the first and second non-shared flow section 162a, 162b, one expansion arrangement 40 is arranged in the common flow path 160. The refrigerant direction in the common flow path 160 is opposite in both operation modes.
• the expansion arrangement 40 comprises at least one bi-directional expansion valve such that the refrigerant can flow through the device in both directions.
• a non-controlled expansion device may be provided.
• a controlled expansion device may be provided with temperature and/or pressure sensor as described before.
• Fig. 18A is a schematic diagram showing the coefficient of performance of the heat pump system (COPsystem) during a washing cycle
• Fig. 18B is a schematic diagram showing the energy consumption of the heat pump system during the washing cycle of Fig. 18A.
• the heating phase corresponds to the first operation mode described herein in which the washing liquid is heated
• the defrosting (regeneration) phase corresponds to the second operation mode in which the washing liquid is cooled.
• the COPsystem may be calculated as follows:
• Eei Heating is the electrical energy supplied to the system in the first operation mode for heating the washing liquid in the tub (e.g. by an electrical heater arranged in the tub),
• Eei Defrosting is the electrical energy supplied to the system in the second operation mode for defrosting the heat exchanging medium (in particular the heat exchanging medium within the tank in which the evaporator is arranged), and
• Eth Heating is the thermal energy which is used for heating the washing liquid during the first operation mode.
• the solid line represents a refrigerant circuit with a fix speed compressor and a single capillary (as shown e.g. in Figs. 15 and 17)
• the dashed line represents a refrigerant circuit with a fixed speed compressor and a double capillary (as shown e.g. in Figs. 14 and 16)
• the dotted line represents a refrigerant circuit with a variable speed compressor (VSC).
• VSC variable speed compressor
• the COPsystem value of each line differs in the defrosting phase.
• the fix speed compressor and the single capillary (solid line) has the lowest COPsystem and the defrosting duration is longer than of the system with the double capillary as the refrigerant flows in the heating an defrosting phase through the same single capillary, and the single capillary is not optimized for the defrosting phase.
• the single capillary is only optimized for the heating phase (since the thermodynamic working conditions such as condensing/ev aporating pressures during the heating and defrosting phase are different) and therefore minimizes only E ei Heating (single capillary cannot be adapted to the defrosting and heating phase).
• the COPsystem value of the fix speed compressor in combination with a double capillary (dashed line) in the defrosting phase is higher and the defrosting phase duration is shorter than of the fix speed compressor and the single capillary (solid line).
• a first capillary of the double capillary is optimized for the heating phase and a second capillary of the double capillary is optimized for the defrosting phase. Therefore, both the Epi Hating and E ei Defrosting are minimized/reduced compared to the single capillary.
• the COPsystem value of the system using a VSC (dotted lined) is higher than of the single and the double capillary in each of the heating and defrosting phase.
• Different compressor speed using the VSC for the heating and defrosting may guarantee the optimal refrigerant flow rate (i.e. desired condensing and evaporating pressures) for each cycle phase in order to minimize E ei Heating and E ei Defrosting.
• the VSC may allow to control the refrigerant flow rate in real time during the washing cycle.
• the refrigerant flow rate through the expansion device can be adjusted by the VSC to the changing thermodynamic conditions, e.g. pressures, even within the heating or defrosting phase (in contrast to a double capillary with fixed speed compressor).
• the defrosting duration of the VSC is longer than of the single and double capillary.
• the defrosting duration may be reduced by reducing the COPsystem by increasing the compressor speed of the VSC.
• the defrosting regeneration
• a quick defrosting by increasing the compressor speed may be applied e.g. when a subsequent washing process in a laundry treatment appliance such as a washing machine/dryer or a dishwasher has been already scheduled by the user e.g. through a user application (APP).
• APP user application
• the energy consumption of the heat pump differs in the defrosting phase.
• the energy consumption of the fix speed compressor with the single capillary has the highest values.
• the energy consumption values of the fix speed compressor with the double capillary are lower than of the fix speed compressor with the single capillary (solid line).
• the energy consumption value of the VSC (dotted line) is significantly lower than of the fix speed compressor with the single capillary (solid line) and the double capillary (dashed line). Therefore, the VSC solution has the best performance compared to the other two solutions with respect to the COPsystem and the energy consumption of the heat pump.
• a controllable expansion device such as a thermostatic or electronic expansion valve may be used instead of a single or double capillary (not shown in Fig 18A and B). This may allow to adjust the refrigerant flow rate in dependency of the (superheating) temperature at the compressor inlet (upstream of the compressor). The refrigerant flow rate may be adjusted in real time. This may allow to adjust proper thermodynamic working conditions for heating and defrosting in order to minimize E Pi H aring and Eei Defrosting (similar to use of double capillary instead of single capillary), and the real time modulation of refrigerant flow rate could be further used for optimization of thermodynamic working conditions in order to minimize electrical energy consumption in real time.
• Fig. 19 is a schematic diagram showing a configuration of a more specific embodiment for the refrigerant flow changing device 78 in the first operation mode
• Fig. 20 is a schematic diagram showing the refrigerant flow changing device of Fig. 19 in the second operation mode.
• the shown refrigerant flow changing device 78 is a four-way-valve 168 comprising a sliding element 170 that is actuated by a refrigerant pressure difference at the two ends of the valve 168 between which the sliding element 170 can move.
• the sliding element 170 operates as a piston which is actuated by selectively applying pressure on the one or the opposite side of the element.
• the sliding element 170 is adapted to slide/switch into a first switching state in which the refrigerant flows in the first flow direction 94a in the first operation mode; and into a second switching/sliding state in which the refrigerant flows in the second flow direction 94b in the second operation mode.
• the refrigerant flow changing device 78 may comprise a three- way-valve 166 that is electrically actuated by a valve such as a solenoid valve 164. As shown in Fig. 20, one pipe of the three-way-valve 166 is connected to the first end of the four-way-valve 168 and another pipe of the three- way- valve 166 is connected to the second end of the four- way- valve 168.
• the three-way-valve 166 may be adapted to move the sliding element 170 by applying a refrigerant pressure to the first or the second end of the valve 166.
• the refrigerant is flowing in the first flow direction (see dashed arrows in Fig. 19) by switching the sliding element 170 to the first switching state (i.e. sliding element is moved to a first position at a first end within the valve 168).
• a first connection pipe 172a is fluidly connected to a second connection pipe 172b
• a fourth connection pipe 172d is fluidly connected to a third connection pipe 172c.
• the refrigerant is flowing from the evaporator 102 via the first connection pipe 172a into the four-way-valve 168, and via the second connection pipe 172b out of the four-way-valve to the inlet 110 of the compressor 36.
• the refrigerant leaving the compressor outlet 112 is flowing through the fourth connection pipe 172d into the four- way- valve and through the third connection pipe 172c out of the four-way-valve 168 and to the condenser 81. From the condenser 81, the refrigerant flows via the expansion valve 40 back to the evaporator 102.
• the refrigerant is flowing in the second flow direction (see solid arrows in Fig. 20) by switching the sliding element 170 to the second switching state (i.e. sliding element is moved to a second position at a second end within the valve 168).
• the first connection pipe 172a is fluidly connected to the fourth connection pipe 172b
• the second connection pipe 172d is fluidly connected to the third connection pipe 172c.
• the refrigerant is flowing from the condenser 81 via the third connection pipe 172c into the four-way-valve 168, and via the second connection pipe 172b out of the four-way- valve 168 to the inlet 110 of the compressor 36.
• Fig. 21 is a schematic diagram showing another configuration of the refrigerant flow changing device in the first operation mode
• Fig. 22 is a schematic diagram showing the refrigerant flow changing device of Fig. 21 in the second operation mode.
• the shown refrigerant flow changing device 78 may be used as an alternative to the refrigerant flow changing device shown in Figs. 19 and 20.
• the refrigerant flow changing device 78 comprises a first refrigerant flow path for the first operation mode and a second refrigerant flow path for the second operation mode, wherein the second refrigerant flow path is at least partially different to the first refrigerant flow path.
• the refrigerant flows in the first flow direction 94a from the evaporator 102 to the compressor inlet 110, from the compressor outlet 112 to the condenser 81, and from the condenser 81 via the expansion valve 40 back to the evaporator 102.
• the refrigerant flows in the second flow direction 94b from the condenser 81 to the compressor inlet 110, from the compressor outlet 112 to the evaporator 102, and from the evaporator 102 via the expansion valve 40 back to the condenser 81.
• the second refrigerant flow path may comprise a pipe branching off the pipe between the condenser 81 and the compressor outlet 112 that is connected to the inlet of the compressor 110 and a pipe branching off the pipe between the evaporator 102 and the compressor inlet 110 that is connected to the outlet of the compressor 112.
• valves 164a, b may be provided for guiding the refrigerant in the first operation mode along the first refrigerant flow path and in the second operation mode along the second refrigerant flow path.
• at least one valve may be provided upstream and one valve downstream of the compressor 36.
• the valves arranged in the second refrigerant flow path are in an off-state 164b (such that the refrigerant can not pass through these valves) and the valves in the first refrigerant flow path are in an on-state 164a (such that the refrigerant can pass through these valves).
• the valves arranged in the first refrigerant flow path are in an off-state 164b (such that the refrigerant can not pass through these valves) and the valves in the second refrigerant flow path are in an on- state 164a (such that the refrigerant can pass through these valves).
• a diverter valve may be arranged at each point at which a pipe of the second refrigerant flow path branches off the pipe of the first refrigerant flow path.
• the diverter valves may be adapted to guide the refrigerant along the first or the second refrigerant flow path.
• the washing liquid exiting the condenser 81 may be directed back to the sump 140.
• the flow diverter 180 may be adapted to direct the washing liquid back into the tub 58, in particular through spray arms 180 which are arranged within the tub 58.
• a first spray arm 180 is arranged in an upper part of the tub 58 and a second spray arm 180 is arranged below the first spray arm, in particular in a lower part of the tub 58.
• the first operation mode comprising the heating of the washing liquid used e.g. during a washing phase of a washing cycle
• the second operation mode comprising the cooling of the washing liquid and thus the heating of the heat exchanging medium 101 within the evaporator tank 102 used e.g. for de-icing the evaporator, in particular during and/or preferably at the end of a rinsing (e.g. the last rinsing phase) of a washing cycle of the dishwasher.
• the refrigerant circuit and arrangement comprising the condenser 81, the expansion arrangement 40, the compressor 36 and the evaporator 102 in the evaporator tank 100, are very similar to the refrigerant circuit of the articles treatment machine such as the washing machine 2 described above. Therefore the features of the respective arrangements for heating/cooling and reverting the refrigerant flow and regarding the first and/or second operation modes as described above are also applicable to a dishwasher.
• the washing liquid is heated by the heated refrigerant when flowing through the condenser 81.
• the washing liquid flows through the sump 140 out of the tub 58 and is circulated via the flow diverter 180 through the condenser 81 in which the washing liquid is heated by the refrigerant and the heated washing liquid is directed back to the tub 58.
• the washing liquid in particular a portion of the washing liquid exiting the sump 140, may be simultaneously directed via a pipe connected to the flow diverter 180 through the spray arms 182 into the tub 58. Thereby the dishes washing/cleaning process already starts while the circulated liquid is simultaneously heated by the heat pump.
• the washing liquid which exits the tub 58 through the sump 140, in particular from a drain manifold which is arranged at the lower part of the sump 140, is drained by the drain pump 72 through the water drain 70.
• the heated washing liquid is cooled when flowing through the condenser 81, wherein the refrigerant is heated by the heated washing liquid.
• the washing liquid flows through the sump 140 out of the tub 58 and is circulated via the flow diverter 180 through the condenser 81 in which the washing liquid is cooled by the refrigerant (and thus the refrigerant is heated) and the cooled washing liquid is directed back to the tub 58.
• the heated refrigerant flows through the evaporator 102 and thereby the heat exchanging medium within the evaporator tank 100 is heated (and preferably deiced) via the refrigerant.
• the cooled-down washing liquid can be drained with the drain pump 72 which is connected to the sump 140, in particular to the drain manifold of the sump 140, through the water drain 70.
• the heater 142 described above with respect to the washing machine 2 may also be provided in the dishwasher 180 inside the tub 58, preferably at the bottom of the tub 58 (e.g. the sump of the tub), for heating the washing liquid.
• the features regarding the heater 142 of the washing machine 2 are also applicable to the dishwasher 180.
• the refrigerant circuit and arrangement of a dishwasher in particular of the dishwasher 180 shown in Fig. 23, is very similar to the refrigerant circuit and arrangement of a laundry treatment machine, and in particular of the above washing machine 2. Therefore, all embodiments disclosed herein regarding the refrigerant circuit and in particular the refrigerant circuit embodiments shown in Figs. 12 to 17 and the different embodiments of the flow changing device 78 shown in Figs. 19 to 22 are equally applicable to a dishwasher and in particular to the dishwasher 180 shown in Fig. 23.
• expansion arrangement expansion device or element
• flow rectifier means e.g. check valve/one-way valve

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• 2022
  • 2022-03-30 EP EP22719549.2A patent/EP4498884A1/de active Pending
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