• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    garment washing machine The present disclosure relates to a heat pump type garment machine in which a second condenser is integrally formed in an evaporator to enhance extra cooling performance, and relates to a garment machine for washing. washing in which a second condenser is integrally added to an evaporator in the garment washing machine employing a heat pump to maximize a condensing effect so as to improve heat exchange efficiency, thereby improving dehumidification capacity in the evaporator with cooling extra refrigerant during the refrigerant cycle. therefore, the garment washing machine of the present disclosure may be a heat pump circulation type garment washing machine including a box, a drum, a drying duct configured to circulate dry air by supplying it, an evaporator having a heat pump, a first condenser, a compressor and an expansion apparatus, wherein the condenser includes a second condenser configured to condense condensed refrigerant from the condenser again so as to extra cool refrigerant during the refrigerant cycle, therefrom mode improving dehumidification capacity in the evaporator.
    公开号:BR102013026926B1
    申请号:R102013026926-3
    申请日:2013-10-18
    公开日:2021-07-20
    发明作者:Seungphyo AHN；Hyunwoo NOH；Hyuksoo Lee
    申请人:Lg Electronics, Inc；
    IPC主号:
    专利说明:

    FUNDAMENTALS OF THE INVENTION 1. Field of invention
    The present disclosure relates to a clothes washing machine, such as a clothes washing machine for washing and drying or a dryer, of the heat pump type, and more particularly, to a clothes dryer for improving the dehumidifying power in an evaporator fitted to a heat pump. 2. Description of the related technique
    In general, a garment washing machine includes a garment handling apparatus, such as a garment washing machine, a washer, a combined washer-dryer, or a dryer. A laundry washing machine having a drying function such as a combined washing and drying machine is a device in which the laundry is inside the drum in a state that washing is completed and a dewatering process is carried out, and supplying hot air into the drum to evaporate moisture from the laundry, thereby drying the laundry.
    For an example of such a dryer, the aforesaid dryer may include a drum rotatably provided within a box for placing garments to be washed therein, a drive motor configured to drive the drum, a blower fan configured to blow air into the drum, and a heating means configured to heat air drawn into the drum. Furthermore, the heating means can use high temperature electrical resistance generated by heat using an electrical resistance, or combustion generated by heat by gas combustion.
    On the other hand, air discharged from the drum contains the moisture of the garment for washing, and thus becomes high-temperature, humid air.
    Here, the dryer can be classified according to a method for processing high-temperature, moist air, and thus divided into a condensing (circulation) type dryer to condense the moisture contained in the high-temperature, moist air by cooling the air below dew point temperature through a condenser while being circulated without discharging high temperature, moist air out of the dryer, and an exhaust type dryer to directly discharge the high temperature, moist air having passed through the drum out.
    In the case of the condensation type dryer in order to condense air discharged from the drum, the process of cooling the air below the dew point temperature must be carried out to heat the air through the heating means before it is supplied to the drum again, Here, the loss of thermal energy contained in the air is generated as it is cooled during the condensation process, and an additional heater or the like is needed to heat the air to a temperature necessary for drying.
    Even in the case of the exhaust type dryer, it is necessary to discharge high temperature and humid air to the outside and to receive outside air at a normal temperature, thus heating the air to the required temperature level through the heating means. In particular, thermal energy transferred by the heating means is contained in high temperature air being discharged to the outside, but it is discharged and wasted to the outside, thereby reducing thermal efficiency.
    Consequently, in recent years, to collect energy needed to generate hot air and energy being discharged to the outside without having been used, clothing care appliances have been introduced to increase energy efficiency, and a clothing care appliance having a system of heat pump was introduced as an example of the clothing treatment apparatus. The heat pump system can include two heat exchangers, a compressor and an expansion apparatus, and energy contained in the hot discharged air is reused in heating air being supplied to the drum, thus increasing energy efficiency.
    Specifically, in the heat pump system, an evaporator is provided on the exhaust side, and a condenser on an inlet side of the drum, and thus thermal energy is transferred to the refrigerant through the evaporator and then thermal energy contained in the refrigerant is transferred to the air drawn into the drum, thereby generating hot air using wasted energy.
    However, in a dryer using such a typical heat pump, the size of the condenser may be restricted due to the lack of space inside which the condenser is installed, thus causing difficulty in achieving its condensing effect.
    Consequently, heat exchange efficiency may be reduced in the heat exchanger and refrigerant cooling may not be properly performed, thus reducing the dehumidification capacity, SUMMARY OF THE INVENTION
    The present disclosure is to solve the aforementioned problems in the related art, and an object of the present disclosure is to provide a garment washing machine, such as a combined washer and dryer or clothes dryer, with improved drying capacity and better energy efficiency .
    As a result of an aspect of the present invention, a garment washing machine such as a combined washer and dryer or dryer machine is provided in which dehumidifying power in an evaporator provided in a heat pump is improved.
    As a consequence of another aspect, a garment washing machine, such as a combined washer and dryer or a dryer, is provided employing a circulation type heat pump in which a second condenser is added to an evaporator for extra. cool, for example, supercooler refrigerant in the refrigerant cycle and maximize a condensation effect, thereby improving heat exchange efficiency. The second condenser can be integrated or integrally formed with the heat pump evaporator.
    Another object of the present disclosure is to provide a garment washing machine, such as a combined washer and dryer or clothes dryer, employing a heat pump structure in which a second condenser is configured with a separate path from the evaporator refrigerant line. . Preferably, the second condenser is arranged at the rear or bottom of the evaporator, thereby promoting improved heat exchange efficiency through cooled dry air or lower condensing water, and thereby, a dehumidification performance can be improved by surrounding 400W.
    According to one embodiment, a heat pump type laundry machine, i.e., a clothes dryer, may include a box; a rotating drum provided inside the box; a drying duct provided in the box to circulate air discharged from the drum by supplying it thereto; an evaporator and a first condenser sequentially provided over a flow path formed by the drying duct; and a compressor and expansion apparatus configured to form a refrigerant cycle together with the evaporator and the first condenser. A laundry washing machine may additionally include a second condenser. The evaporator, the compressor, the first condenser, the second condenser and the expansion apparatus can form a garment washing machine heat pump having a second conservator.
    Preferably, a heat pump type washing machine, i.e., clothes dryer, includes: a box, a rotating drum provided inside the box, a drying duct provided in the cabinet for circulating discharged air from the drum for restoring it to it; an evaporator and a first condenser sequentially provided in a flow path formed by a drying duct; and a compressor and expansion apparatus configured to form a refrigerant cycle across the evaporator and the first condenser, wherein:
    The evaporator comprises the second condenser. The second condenser can be configured to condense condensed refrigerant from the first condenser again. In an exemplary embodiment, the evaporator refrigerant tube and the second condenser refrigerant tube can be formed by penetrating the same heat dissipation fins. By these means, the refrigerant can be extra cooled during the refrigerant cycle, thus improving dehumidification capacity in the evaporator.
    The refrigerant tube of the second condenser can be arranged on the rear side with respect to the dry air flow direction. In addition, the evaporator refrigerant tube and the second condenser refrigerant tube can be formed on the same heat dissipation fins.
    In accordance with an embodiment of the present disclosure, the evaporator refrigerant tube may be arranged vertically, for example, in a tortuous pattern or a zigzag pattern. In this case, the lower end portion of the evaporator refrigerant tube can be disposed above or over the condensing water line. Additionally, and the second condenser refrigerant tube can be arranged vertically, for example, in a tortuous pattern or in a zigzag pattern on the back side with respect to the dry air flow direction. Alternatively, the second condenser refrigerant pipe may be arranged horizontally below a portion of the evaporator, such that the second condenser refrigerant pipe is at least partially arranged below a condensing water line and may be at least partially submerged. , below a condensed water line and can be submerged, at least partially, in condensed water. The second capacitor is a separate structure, that is, independent of the structure of the first capacitor. So the second condenser can be arranged in a different position than the first condenser.
    As an aspect of the present disclosure, the evaporator refrigerant pipe, i.e., the refrigerant pipe or piping, may be configured as one way. Here, the second condenser refrigerant tube can be formed as a second way, that is, with an independent refrigerant line separate from the evaporator refrigerant flow path.
    In one embodiment, the refrigerant tube or refrigerant tube via the evaporator can be formed with a path arranged vertically, for example in a zigzag pattern, with many columns, and the refrigerant tube or refrigerant path the refrigerant tube of the second condenser can be formed with a route arranged vertically, for example in a zigzag pattern with a column. However, the refrigerant tube or the second condenser path can also have more than one column,
    According to another embodiment of the present disclosure, the evaporator refrigerant tube may be arranged vertically, for example, in a zigzag pattern. Additionally, the refrigerant tube of the second condenser can be arranged horizontally, in a zigzag pattern. Preferably, the refrigerant pipe of the second condenser is arranged in the lower portion of the evaporator, i.e. to be submerged under condensing water below a condensing water line. In accordance with the present disclosure, the first condenser, second condenser, expansion apparatus, evaporator and compressor are connected to circulate refrigerant along a refrigerant circulation line so as to form a heat pump refrigerant cycle. Here, the following condenser can be arranged between the first condenser and the expansion apparatus along the refrigerant circulation line.
    In addition, the refrigerant cycle may include a second condensing operation on refrigerant (P2) exiting the first condenser through the second condenser to increase the degree of extra cooling of the refrigerant (P3) exiting the second condenser.
    The heat pump can be configured such that the enthalpy of the refrigerant (P3) leaving the second condenser is less than that of the refrigerant (P2) leaving the first condenser.
    According to the present disclosure, evaporator dehumidification performance can be improved by 400 W during the refrigerant cycle due to a difference (ΔQ) between the refrigerant enthalpy (P2) leaving the first condenser and the refrigerant enthalpy (P3) coming out of the second condenser.
    Preferably, a heater for reheating air can be configured to be additionally provided in the washing machine, for example to reheat air that has been heated while passing through the evaporator. The heater can be arranged in the drying duct or in an inlet duct to supply heated air to the drum.
    As described above, in accordance with the present disclosure, the following effects can be promoted by the aforementioned task solving means, and the configurations, combinations, and working relationships that will be described later.
    In accordance with the present disclosure, a second condenser may be integrally added to an evaporator in a garment washing machine employing a circulation type heat pump to extra cool refrigerant in the refrigerant cycle and maximize a condensing effect, thereby enhancing the heat exchange efficiency.
    In accordance with the present disclosure, a second condenser can be configured via a separate path from the evaporator refrigerant line at the rear end or lower end of the evaporator, thereby improving dehumidification performance around 400W due to condensed water cooling according to improved heat exchange efficiency. BRIEF DESCRIPTION OF THE FIGURES
    The accompanying illustrations, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and, together with the description, serve to explain the principles of the invention. In the illustrations:
    FIG. 1 is a schematic view illustrating the internal structure of a heat pump type dryer in accordance with the present invention; FIG. 2 is a partial detail view illustrating a circulation type heat pump inside the dryer shown in FIG. 1; FIG. 3 is a structural view illustrating the method of drying the heat pump; FIG. 4 is a view illustrating the refrigerant circulation path of an evaporator in a heat pump in the related art;
    FIG. 5 is a block diagram illustrating the refrigerant circulation path using a second condenser integrated with an evaporator in accordance with the present disclosure; FIGS. 6 and 7 are views illustrating a refrigerant circulation path in an evaporator and a second condenser integrated with an evaporator in accordance with the present disclosure; and FIG. 8 is a graph showing improved dehumidification performance in accordance with improved heat exchange efficiency in the present disclosure. DETAILED DESCRIPTION OF THE INVENTION
    Hereinafter, a heat pump type dryer according to a preferred embodiment of the present disclosure will be described in detail with reference to the attached figures. The dryer is just one example of a garment washing machine according to the present disclosure. The same applies for a combined washer-dryer or similar.
    Before the description, it should be noted that the terms and words used in the description and claims should not be limited and interpreted as being typical or literal, and should be interpreted as meaning and concept as per the technical concept of the invention based on that the inventor can define the concept of terms and words to describe the invention in a better way.
    Consequently, since the embodiments described in the present disclosure and configurations shown in the figures are the most preferred embodiments only and do not represent all of the technical concepts of the invention, it should be understood that there may be several equivalent and modification examples that can replace them at the time of applying this disclosure.
    Hereinafter, the configurations and working relationships of a clothes dryer as an example for a washing machine according to the present disclosure will be described in detail with reference to the attached figures.
    FIGS, 1 and 2 are views illustrating the internal structure of a heat pump type dryer in accordance with the present invention, and FIG. 3 is a block diagram illustrating the heat pump drying method FIG, 4 is a view illustrating the refrigerant circulation path of an evaporator in a heat pump in the related art.
    Furthermore, FIG. 5 is a block diagram illustrating the refrigerant circulation path using a second condenser integrated with an evaporator in accordance with the present disclosure, and FIGS. 6 and 7 are views illustrating a refrigerant circulation path in an evaporator and a second condenser integrated with an evaporator in accordance with the present disclosure.
    Furthermore, FIG. 8 is a graph showing improved dehumidification performance in accordance with improved heat exchange efficiency in the present disclosure.
    With reference to FIGS. 1 to 3, the present disclosure may include a box 100 forming the exterior of the clothes dryer, and a rotating drum 110 provided within the box. The drum is rotatable supported by a support (not shown) on the front and rear sides of the drum and can be driven by a 10 motor.
    An inlet duct 170 provided in the casing to draw outside air and supply the air to an inner portion of the drum is provided in the vertical direction of the drum on the rear side of the drum. The inlet flow path through which the air drawn into the drum flows is formed by the inlet duct. In accordance with the present disclosure, air drawn through the inlet duct can be drawn in from outside the box separately from the drying duct 190.
    On the other hand, a heater 180 to heat the aspirated air to take it high-temperature air needed to dry the garment for washing can be provided inside the inlet duct 170. The heater 180 receives electrical energy to provide heat to be supplied sufficiently and quickly to the drum, and additionally provides heating such that the refrigerant cycle is stably controlled in a normal state. By these means, energy efficiency of a heat pump type garment washing machine can be improved and a heat pump overload situation can be avoided.
    According to the aforementioned structure, the heat needed for drying can be sufficiently supplied in a short period of time, thus having a drying time-reducing effect. In other words, additional heating can be provided in a short period of time since the heating cannot be sufficiently supplied in a short period of time using only air in the circulation flow path with the drying duct.
    Air drawn into the drum can be supplied through a circulation flow path formed in drying duct 190 separately from the air through the inlet flow path. The drying duct 190 is provided in the box to circulate air discharged from the drum when supplying it thereto.
    Air drawn into the drum dries the garment for washing and is then drawn into a front surface duct (not shown) located on a lower front side of the drum and supplied to the drum again through the drying duct by means of a filter of fiber (not shown) or discharged to the outside of the box through an exhaust duct that will be described later.
    A blower fan 120 to draw air into the drum to forcibly draw it out of the dryer can be provided in the circulation flow path of the drying duct.
    Here, an evaporator 130 and a condenser 140 are sequentially provided in a flow path formed by the drying duct. Evaporator 130 and condenser 140 as a heat exchanger type, according to the present disclosure, form a heat pump refrigerant cycle, thereby achieving heat exchange with air (Ad) in the circulation flow path by refrigerant flowing in the inside him.
    The air taken into the drum is heated by heater 180 in the inflow path or condenser 140 in the circulating flow to make it dry high temperature air at about 150-250°C when being taken in. of the drum. High temperature air is brought into contact with an object to be dried to evaporate moisture from the object to be dried. Evaporated moisture is to be contained in medium temperature air and exhausted out of the drum. At this point, in order to circulate the moist, medium temperature air and reuse it, the moisture must be removed. Since the moisture content in the air is affected by temperature, moisture can be removed by cooling the air. Consequently, the air in the circulation flow path is cooled by heat exchange with the evaporator 130.
    In order to supply the air cooled by the evaporator 130 back to the drum, it must be heated by high temperature air, and the air heating is performed by the condenser 140.
    A refrigerant cycle performs heat exchange with the environment using the phase change of refrigerant flowing through the inner side of the refrigerant. Briefly described, the refrigerant is transformed into a low-temperature, low-pressure gas by absorbing heat from the environment in the evaporator, compressed into a high-temperature, high-pressure gas in the compressor, transformed into a high-temperature, high-pressure liquid by dissipating of heat to the environment in the condenser, transformed into a liquid of low temperature and low pressure by the drop of its pressure in the expansion apparatus, and is taken to the evaporator again. Due to the refrigerant circulation, heat is absorbed from the environment in the evaporator and heat is supplied to the environment in the condenser. The refrigerant cycle can also be referred to as a heat pump.
    In accordance with the present disclosure, the refrigerant cycle may include compressor 150 and expansion apparatus 160 along with evaporator 130 and condenser 140.
    The air flow path in heat exchange with the refrigerant cycle is illustrated in FIGS. 2 and 3. In other words, an arrow passing through the evaporator and condenser and a line connecting between the evaporator and condenser does not indicate the refrigerant flow path, but does indicate the air flow path in FIGS. 2 and 3, and the air is sequentially brought into contact with the evaporator and the like to perform heat exchange.
    For the configuration in more detail, as illustrated in FIG. 3, it is seen that evaporator 130 and condenser 140 are sequentially disposed, respectively, in the circulation flow path (a large circulation line formed along a bold arrow in FIG. 3) formed by the drying duct 190.
    As illustrated in FIG. 3, the air (Ad) in the circulation flow path performs heat exchange with the heat pump during the refrigerant cycle, specifically the air (Ad) in the circulation flow path dissipates heat in heat exchange with the evaporator, and absorbs heat in exchange for heat with the condenser. As a result, the air in the circulation flow path absorbs heat dissipated by itself again.
    In general, the evaporator and condenser are mainly responsible for the heat exchange during the refrigerant cycle, and the air from which heat is taken in the evaporator liquefies the moisture contained in it to exhaust it as condensation water, and dry air is heated by the compressor and condenser to be changed into high temperature dry air.
    In this way, the air exchanged into high temperature air in heat exchange with the refrigerant cycle through the circulation flow path is taken into the drum along with the air in the inlet flow path to participate in the drying process.
    Here, part of the air taken into the drum and used in the drying process is exhausted to the outside of the dryer, and part of it is reused, and supplied to the reused air by absorbing only part of the heat wasted using the refrigerant cycle. However, embodiments of the present invention may also be employed in an interface diaphragm circulating type dryer without exhaust air or in an exhaust air type dryer in which all air is exhausted out of the dryer.
    In the heat pump type clothes dryer, waste heat is typically collected using the refrigerant cycle, and the present disclosure provides a means of optimizing not to cause an overload during the refrigerant cycle. In other words, in the case of a refrigerant cycle, the refrigerant heat exchange must be carried out by the phase change at the ideal operating temperature and pressure, and for this purpose, a heat exchanger such as an evaporator and a condenser, a compressor, an expansion apparatus and the like are used. Consequently, in order to collect more heat, the size of the heat exchanger or compressor is inevitably increased. However, in the case of a typical clothes dryer, it has a spatial restriction and therefore the heat exchanger, compressor or the like is limited in size.
    Accordingly, in accordance with the present disclosure, heater 180 for heating the drawn in air to make it high temperature air necessary for drying laundry garments is provided within the inlet duct to continuously replenish the drawn in air with heat.
    In accordance with the present disclosure, heat can be replenished through heater 180 to sufficiently provide the heat needed for drying, thereby reducing drying time. Furthermore, in the case of a refrigerant cycle, the refrigerant heat exchange must be carried out by a phase change at the optimum operating temperature and pressure and, for that purpose, heating must be sufficiently supplied. Otherwise, this can cause a problem, such as a refrigerant being supplied to the compressor in a liquid phase or the like, and therefore the cycle cannot be stably operated, thus reducing cycle reliability. Consequently, as disclosed herein, the air carried into the drum can be further replenished with heating by heater 180, and it is preferable that the refrigerant cycle can be stably operated in a normal state.
    Additionally, an additional blower fan 120 can be provided in the inlet flow path to provide more airflow. Furthermore, the additional blower fan provides more airflow and thus the heater 180 is not overheated in the inflow path. The configuration provided with the additional blow fan 120 is illustrated in FIGS. 2 to 4.
    On the other hand, the present disclosure can be configured such that part of the air is exhausted out of the box upstream of the evaporator in the circulation flow path. Consequently, as illustrated in FIG. 1, the present disclosure may additionally include an exhaust duct 15 branched from the evaporator upstream 130 into drying duct 190, and the exhaust duct is configured to exhaust some of the air out of the box upstream of the evaporator in the track. of circulation flow. The exhaust duct forms an exhaust flow path to discharge hot air exiting the drum to exhaust some of the air to the outside of the box.
    According to the aforementioned configuration, waste heat is absorbed from part of the moist, medium temperature air leaving the drum only within a range that can be processed by the refrigerant cycle, and the rest of the air is exhausted. Consequently, it may be possible to reduce energy waste as well as not cause an overload during the refrigerant cycle. Furthermore, it may be possible to reduce energy consumption as well as increase reliability for the operation of the refrigerant cycle.
    Hereinafter, a heat pump type clothes dryer in which a second condenser according to the present disclosure can be installed in the evaporator to maximize a condensing effect so as to improve dehumidification capability in the evaporator will be described with reference to FIGS. 4 to 7.
    Referring to FIG. 4, the evaporator 130 in the related art is formed over a one-way refrigerant with an inlet 131 and an outlet 132 respectively, and the evaporator piping line passing through a plurality of superimposed plate-shaped heat dissipation fins is vertically designed in a zigzag pattern.
    Refrigerant led to the inlet 131 of the evaporator refrigerant tube of expansion apparatus 160 flows along the evaporator refrigerant line to perform heat exchange. In addition, the refrigerant from the evaporator tube that has completed heat exchange is circulated to the compressor 150 through the outlet 132 of the evaporator refrigerant tube 130.
    In such a refrigerant cycle in the related art, the evaporator 130 simply performs a heat exchange operation with high temperature, moist air in the dryer to reduce the air temperature and extract condensed water. In addition, air flowing through the condenser 140 is heated to allow the high temperature, moist air to flow into the drum again.
    Because of this, in accordance with the present disclosure, condenser 140 is used as a first condenser, and a second condenser 141 is provided in evaporator 130 to further enhance a heat exchange provided by condenser 140, thereby improving exchange efficiency. of heat with air.
    During the refrigerant cycle, refrigerant passes through compressor 150 to follow the circulation path through condenser 140, expansion apparatus 160 and evaporator 130. According to the present disclosure, refrigerant that has passed through compressor 150 is condensed in condenser 140 , and then condensed again in the second condenser 141 provided separately in the evaporator 130, thus enhancing its condensing effect.
    Referring to FIG. 5, evaporator 130 may include second condenser 141 configured to condense refrigerant (P2) condensed from condenser 140 again. Refrigerant (P3) condensed again in second condenser 141 is circulated to expansion apparatus 160. In addition, refrigerant (P4) exiting expansion apparatus is circulated along evaporator refrigerant pipe 130 to extra cool refrigerant during the refrigerant cycle , thus improving dehumidification capacity in the evaporator.
    Thereafter, the refrigerant (P5) coming through the evaporator 130 passes through the compressor 150, and the compressed refrigerant (P1) flows into the refrigerant tube of the condenser 140 again, thereby allowing the refrigerant cycle to be circulated in the refrigerant cycle.
    Furthermore, as illustrated in FIGS. 5 and 6, the evaporator refrigerant tube 130 and the second condenser refrigerant tube 141 are formed on the same heat dissipation fins.
    The heat dissipation fins are formed in such a way that a plurality of plate-shaped materials with excellent thermal conductivity are superimposed on each other to efficiently perform external heat exchange with the refrigerant tube refrigerant.
    In this way, according to the present disclosure, the degree of extra cooling can be further increased through the first operation of the condenser 140 and the second condensing of the second condenser 141 to improve the dehumidification capacity in the evaporator, thereby improving pump efficiency. of heat.
    The refrigerant cycle in a condenser type dryer heat pump according to the aforementioned modality enhances dehumidification capability in the evaporator to remove moisture in the dry flow path. To this end, the refrigerant flowing into the pipe from the outgoing condenser passes through the second condenser without first passing through the expansion apparatus (or expansion valve). Consequently, it has a structure in which refrigerant in the second condenser 143 is further extra cooled and brought to the evaporator in a state of low refrigerant dryness or low refrigerant temperature through the expansion apparatus (eg expansion valve), thereby improving the dehumidification capacity.
    The second condenser 141 according to the present disclosure can be arranged vertically on a rear side of the evaporator 130 (in the air flow direction) or horizontally on a lower side thereof, i.e. below the evaporator 130; For example, the second evaporator 141 may be piped in a vertical orientation (perpendicular) to the rear end of the evaporator 130 or piped in a horizontal orientation in the bottom column thereof as illustrated in FIGS. 6 and 7. Vertical or horizontal refers to the main flow direction of refrigerant in the refrigerant pipe. For example, if the evaporator 130 is arranged vertically and has four columns, as shown in FIG. 6, the columns being arranged vertically.
    FIGS. 6 and 7 are views illustrating the refrigerant flow path structure of an evaporator in which an additional refrigerant pipe is independently piped in place of the second condenser 141.
    According to an embodiment of the present disclosure illustrated in FIG. 6, the evaporator refrigerant tube 130 is arranged vertically in a zigzag pattern, and the lower end portion of the evaporator refrigerant tube 130 is disposed above or in the condensing water line. Here, the second condenser refrigerant tube 141 can be arranged vertically in a zigzag pattern on the back side of the evaporator 130 with respect to the dry air flow direction.
    In this way, the position of the second condenser refrigerant tube 141 is to maximize heat exchange efficiency, as moisture is removed and the temperature is reduced in air (Ad), while air has high temperature and humid air (Ad) first passes through, for example, evaporator 130, then through second condenser 141 before passing through condenser 140.
    As an aspect of the present disclosure, the evaporator refrigerant pipe 130 is configured with one way, and the second condenser refrigerant pipe plumbing path 141 is formed with an independent refrigerant line separate from the refrigerant flow path 130.
    The evaporator refrigerant tube 130 can be formed with a path arranged vertically in a zigzag pattern with a plurality of columns, and (in FIG. 6 four columns) and the second condenser refrigerant tube 141 can be formed with a path arranged vertically in a zigzag pattern with one or more columns.
    In particular, the embodiment of FIG. 6 illustrates a structure in which on the front side (left side in the illustration) first through four evaporator columns 130 are used for the evaporator refrigerant tube 130 responsible for refrigerant dehumidification and air cooling, and the last fifth column on the rear side (right side in illustration) is used as the second condenser refrigerant tube 141 to increase the degree of extra cooling of the refrigerant.
    Here, refrigerant is evaporated in the evaporator refrigerant tube 130 (primarily through the four columns on the front side) to transfer the heat of vaporization to the external high temperature humid air (Ad), thus allowing steam in the air to condense in water. Consequently, dry air at room temperature that has passed through the evaporator 130 is heat exchanged in the second condenser 141 through the refrigerant in a portion of the evaporator 130 (fifth column on the back side) used for the second condenser 141, thereby increasing the degree second condenser refrigerant extra coolant 141.
    In accordance with another embodiment of the present disclosure illustrated in FIG. 7, the evaporator refrigerant tube 130 is arranged vertically in a zigzag pattern, and the second condenser refrigerant tube 141 is arranged to be submerged under condensing water below a condensing water line in a lower portion of the evaporator 130, and arranged horizontally in a zigzag pattern.
    In this way, according to a structure in which a lower portion of the evaporator 130 which is a heat exchanger is used by the second condenser 141, the heat from vaporization in an upper portion of the evaporator 130 which is a heat exchanger is transferred and the generated condensate water flows downwards due to gravity. Since the second condenser 141 is installed in the lower portion, the degree of extra cooling is increased due to a temperature difference between condensing water and refrigerant while passing through the second condenser 141.
    Hereinafter, improved dehumidification performance in an evaporator via a second condenser mounted on the evaporator in accordance with the present disclosure will be described in detail with reference to FIGS. 6 to 8.
    According to the present disclosure, condenser 140 is used for a first condenser which is a heat pump system, second condenser 141, expansion apparatus 160, evaporator 130 and compressor 150 are connected to circulate refrigerant along a refrigerant circulation line to form a refrigerant cycle.
    Also, as illustrated in a graph in FIG. 8, the refrigerant cycle can perform a second condensing operation on refrigerant (P2) exiting the condenser 140 through the second condenser 141 to increase the degree of extra cooling of the refrigerant (P3) exiting the second condenser by ΔQ.
    In other words, the enthalpy of the refrigerant (P3) leaving the second condenser 141 is formed to be less than that of the refrigerant (P2) leaving the condenser 140.
    Referring to FIGS. 6 to 8, according to the present disclosure, the dehumidification performance of the evaporator 130 can be improved by 400 W during the refrigerant cycle due to a difference (ΔQ) between the refrigerant enthalpy (P2) leaving the condenser 140 and the enthalpy of the refrigerant (P3) leaving the second condenser 141.
    As shown in a graph of FIG. 8, firstly, when a first condensing operation is performed in condenser 140 in state (1) which is a phase of the refrigerant (P1) leaving compressor 150, it has the phase changed to the location of (2) (refrigerant in phase of P2) . Then, an extra degree of cooling using the second condenser 141 according to the present disclosure is increased to the location of (3) (refrigerant in the P3 stage) from that of (2) (refrigerant in the P2 stage). Consequently, heat absorption start location in evaporator 130 is moved to location (4) (P4), and thus it is seen that dehumidification performance is improved from 2600 W in the related technique to 3000 W, enthalpy (4 ) for enthalpy (5), around 400 W.
    As a result, according to the present disclosure, the following effects can be promoted by the aforementioned task solving means, and the configurations, combinations, and working relationships that will be described later.
    In accordance with the present disclosure, the second condenser 141 may be integrally added to the evaporator 130 in a garment washing machine employing a circulation type heat pump to extra cool refrigerant in the refrigerant cycle and maximize a condensing effect, thereby improving heat exchange efficiency.
    In addition, the second condenser 141 can be configured via a separate path from the evaporator refrigerant line in the rear or lower portion of the evaporator 130, thereby improving dehumidification performance around 400 W due to condensed water cooling accordingly. with improved heat exchange efficiency.
    The aforementioned embodiments are merely preferred embodiments of the present disclosure to enable persons ordinarily skilled in the art to which the present disclosure belongs (hereinafter, referred to as "those skilled in the art") to easily implement a clothes dryer having an evaporator provided with a second condenser according to the present disclosure, and the present disclosure is not limited to the aforementioned embodiments and the attached illustrations, and thus the scope of rights of the present disclosure is not limited thereto. Consequently, it should be understood by those skilled in the art that various substitutions, modifications and changes can be made without deviating from the technical concept of the invention, and it should be clearly understood that portions that can be easily changed by those skilled in the art will fall within the scope of the rights of the invention.
    权利要求:
    Claims (10)
    [0001]
    1. Garment washing machine, comprising: a rotating drum (110); a drying duct (190) configured to circulate air discharged from the drum (110) by supplying it thereto; an evaporator (130) and a first condenser (140) sequentially provided in a flow path formed by the drying duct (190); a compressor (150) and an expansion apparatus (160) configured to form a refrigerant cycle together with the evaporator (130) and the first condenser (140), and a second condenser (141) configured to receive condensed refrigerant from the first condenser (140) and condense the received refrigerant again, characterized in that the second condenser (141) is formed integrally with the evaporator (130), and a second condenser refrigerant tube (141) is arranged to be submerged under water from condensation in a lower portion of the evaporator (130).
    [0002]
    2. Garment washing machine according to claim 1, characterized in that the evaporator refrigerant tube (130) and the second condenser refrigerant tube (141) are formed on the same heat dissipation fins.
    [0003]
    3. Garment washing machine according to claim 1 or 2, characterized in that an evaporator refrigerant pipe (130) is configured as one way, and the second condenser refrigerant pipe (141) is formed as a independent refrigerant line separate from evaporator refrigerant tube (130).
    [0004]
    4. Garment washing machine according to any one of claims 1 to 3, characterized in that the evaporator refrigerant tube (130) is arranged vertically in a zigzag pattern.
    [0005]
    5. Garment washing machine according to claim 4, characterized in that the evaporator refrigerant tube (130) is formed with one way in a zigzag pattern with many columns.
    [0006]
    6. Garment washing machine according to any one of claims 1 to 5, characterized in that the refrigerant tube of the second condenser (141) is arranged horizontally.
    [0007]
    7. Garment washing machine according to any one of claims 1 to 6, characterized in that the first condenser (140), the second condenser (141), the expansion apparatus (160), the evaporator (130 ) and the compressor (150) are connected to circulate refrigerant along a refrigerant circulation path so as to form a refrigerant cycle.
    [0008]
    8. Garment washing machine according to claim 7, characterized in that the second condenser (141) is arranged between the first condenser (140) and the expansion apparatus (160) in the refrigerant cycle.
    [0009]
    9. Clothes washing machine according to claim 7 or 8, characterized in that the refrigerant cycle performs a second condensing operation on the refrigerant (P2) leaving the first condenser (140) through the second condenser (141).
    [0010]
    10. Clothing washing machine, according to any one of claims 1 to 9, characterized in that an enthalpy of refrigerant (P3) leaving the second condenser (141) is smaller than that of refrigerant (P2) leaving the first condenser (140).
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    同族专利:
    公开号 | 公开日
    AU2013245520A1|2014-05-08|
    RU2557737C2|2015-07-27|
    KR20140050982A|2014-04-30|
    EP2725132A2|2014-04-30|
    BR102013026926A2|2014-08-19|
    AU2018100480A4|2018-05-17|
    AU2018100480B4|2019-11-07|
    RU2013142950A|2015-03-27|
    EP2725132A3|2016-03-30|
    KR101987695B1|2019-06-11|
    DE202013104698U1|2014-01-29|
    US20140109426A1|2014-04-24|
    US9207015B2|2015-12-08|
    AU2013245520B2|2018-01-18|
    EP2725132B1|2019-07-31|
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    法律状态:
    2014-08-19| B03A| Publication of a patent application or of a certificate of addition of invention [chapter 3.1 patent gazette]|
    2018-03-06| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2018-03-13| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2018-03-20| B06I| Publication of requirement cancelled [chapter 6.9 patent gazette]|Free format text: ANULADA A PUBLICACAO CODIGO 6.6.1 NA RPI NO 2462 DE 13/03/2018 POR TER SIDO INDEVIDA. |
    2019-08-27| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2021-05-11| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2021-07-20| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 18/10/2013, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    KR10-2012-0117469|2012-10-22|
    KR1020120117469A|KR101987695B1|2012-10-22|2012-10-22|A clothes dryer having an evaporator equipped with the second condenser|
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