• 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:
    clothing treatment apparatus. a clothing treatment apparatus includes: an accommodation chamber (110) in which an object is accommodated; a first heat pump cycle (140) having a first evaporator (141), a first compressor (143), a first condenser (142) and a first expansion valve (144); a second heat pump cycle (150) having a second evaporator (151), a second compressor (153), a second condenser (152) and a second expansion valve (154), and arranged such that air is introduced into the chamber (110) passes through the first evaporator (141), the second evaporator (151), the second condenser (152) and the first condenser (142), sequentially; and a controller configured to control an operation of the first and second cycles of the heat pump (140, 150), wherein at least one of the first and second compressors (143, 153) is provided with an inverter for changing the speed. driving the compressor (143, 153) through a frequency conversion, and wherein the controller drives at least one of the first compressor (143) and the second compressor (153) within a predefined drive range by controlling the drive speed of at least one of the first and second compressors (143, 153) using the inverter.
    公开号:BR102015032731B1
    申请号:R102015032731-5
    申请日:2015-12-28
    公开日:2022-01-11
    发明作者:Byeongjo Ryoo；Daeyun Park；Yongju LEE
    申请人:Lg Electronics Inc；
    IPC主号:
    专利说明:

    FUNDAMENTALS OF THE INVENTION 1. Field of Invention
    [0001] The present invention relates to a garment care apparatus and more particularly, a garment care apparatus having a heat pump cycle for drying clothes, etc. 2. Fundamentals of the Invention
    [0002] Generally speaking, a clothes dryer having a drying function, such as a washing machine or dryer, is an apparatus for drying clothing by evaporating moisture contained in the clothing by blowing a hot blast generated by a heater into a drum.
    [0003] The clothes dryer can be classified into an exhaust type clothes dryer and a condenser type clothes dryer according to a method of processing wet air passing through a drum after drying garments.
    [0004] In the exhaust type clothes dryer, moist air passing through a drum is expelled out of the clothes dryer. On the other hand, in a condenser-type clothes dryer, moist air passing through a drum is circulated without being blown out of the clothes dryer. Then, the moist air is cooled to a temperature below a dew point temperature by a condenser, so moisture included in the moist air is condensed.
    [0005] In the condenser type clothes dryer, condensed water, condensed by a condenser, is heated by a heater, and then heated air is introduced into a drum. As moist air is cooled to be condensed, heat energy from the air is lost. In order to heat the air to a temperature high enough to dry clothes, additional heating is required.
    [0006] In the exhaust type clothes dryer, high temperature and high humidity air should be blown out of the clothes dryer, and the outside ambient temperature air should be introduced to be heated to a temperature required by a heater. As drying processes are carried out, air discharged from a drum outlet has low humidity. The air is not used to dry clothes, but is instead blown out of the clothes dryer. As a result, an amount of heat from the air is lost. This can degrade thermal efficiency.
    [0007] Recently, a clothes dryer having a heat pump cycle, capable of enhancing energy efficiency by collecting energy discharged from a drum and heating the air introduced into the drum using the energy, has been developed.
    [0008] The condenser-type clothes dryer having the heat pump cycle may include a drum into which garments can be introduced, a circulation duct providing a passage such that air circulates through the drum, a circulation fan configured to move circulating air along the circulating duct, and a heat pump cycle having an evaporator and condenser installed serially along the circulating duct such that air circulating along the circulating duct passes through of the evaporator and condenser.
    [0009] The heat pump cycle may include a circulation tube, which forms the circulation passage, such that a refrigerant fluid circulates through the evaporator and condenser, and a compressor and an expansion valve installed along the tube. circulation between the evaporator and the condenser.
    [0010] In the heat pump cycle, heat energy from air passing through the drum can be transferred to a refrigerant fluid through the evaporator, and then the heat energy from the refrigerant fluid can be transferred to the air introduced into the cylinder through the condenser. With such a configuration, a hot blast can be generated using thermal energy discarded by the conventional exhaust type clothes dryer or lost in the conventional condenser type clothes dryer. In this case, a heater for heating heated air as it passes through the condenser may additionally be included.
    [0011] Clothes dryer using heat pump cycle can have more effective dehumidification function by drying method using heat pump cycle instead of conventional method due to its high energy efficiency. SUMMARY OF THE INVENTION
    [0012] Therefore, one aspect of the detailed description is to provide a garment treatment apparatus having a heat pump cycle, capable of reducing a drying time by increasing the dehumidification function.
    [0013] Another aspect of the detailed description is to provide a garment care apparatus having a multicycle heat pump, and capable of being operated in a wide range of drive conditions.
    [0014] Another aspect of the detailed description is to provide a garment treatment apparatus capable of matching each cycle of a single heat pump and a multicycle heat pump.
    [0015] In order to achieve these and other advantages and in accordance with the purpose of this specification, as modalized and broadly described in this document, a garment treatment apparatus is provided including: an accommodation chamber, in which an object is accommodated; a first heat pump cycle having a first evaporator, a first compressor, a first condenser and a first expansion valve; a second heat pump cycle having a second evaporator, a second compressor, a second condenser and a second expansion valve, and arranged such that air introduced into the accommodation chamber passes through the first evaporator, the second evaporator, the second condenser and from the first capacitor, sequentially; and a controller configured to control an operation of the first and second cycles of the heat pump, wherein at least one of the first and second compressors is provided with an inverter for changing a drive speed of the compressor through a frequency conversion , and wherein the controller drives at least one of the first compressor and the second compressor within a predefined drive range by controlling the drive speed of at least one of the first and second compressors using the inverter.
    [0016] In an embodiment of the present invention, at least one of the first compressor and the second compressor can be driven in a first mode where the drive speed is constant as a first speed and a second mode where the drive speed is varied from first speed to second speed. When at least one of a peripheral temperature, object quantity and an initial moisture content (BMI) amount of the object is outside a specific range, the controller can control at least one of the first compressor and the second compressor to be activated in the second mode.
    [0017] In one embodiment of the present invention, an inverter drive frequency can be controlled to be reduced at a specific time when at least one of the peripheral temperature, the object quantity, and the initial moisture content amount (BMI) of the object is greater than an upper bound value or lower than a lower bound value within the specified range.
    [0018] In an embodiment of the present invention, in a case where at least one of the peripheral temperature, the amount of the object and the amount of initial moisture content (BMI) of the object is greater than an upper limit value within the range specific, the first and second compressors can have the same drive speed in the first mode, and one of the first and second compressors that has an inverter can have its drive speed reduced in the second mode.
    [0019] In one embodiment of the present invention, at least one of the first and second compressors can be driven in the first and second modes and then can be driven in a third mode where the drive speed is maintained as the second speed.
    [0020] In one embodiment of the present invention, the controller can control the drive speed of at least one of the first and second compressors, based on a condenser condensing temperature or a compressor discharge temperature, the detected temperature in at least one of the first and second heat pump cycles. If the condensing temperature of the condenser or the discharge temperature of the compressor is outside a predefined range, the controller can determine that at least one of a peripheral temperature, the amount of the object, and the amount of initial moisture content (IMC) of the object is outside a specific range.
    [0021] In one embodiment of the present invention, the preset drive range may indicate a compression ratio range, and the second compressor may be formed to have a higher compression ratio than the first compressor. The second compressor can be provided with an inverter, and the first compressor can be driven at a constant speed.
    [0022] In order to achieve these and other advantages and in accordance with the purpose of this specification, as modalized and broadly described in this document, a garment treatment apparatus is also provided, including: a drum in which an object is accommodated; at least one evaporator; at least one condenser configured to heat air introduced into the drum; at least one compressor configured to form a heat pump cycle by being combined with at least one condenser and at least one evaporator; and a base frame including a first accommodation portion for accommodating the at least one evaporator and the at least one condenser, a second accommodation portion arranged parallel to the first accommodation portion and for accommodating the at least one compressor and a formed wall. for dividing the first and second accommodation portions from each other such that a flow path is formed in the first accommodation portion.
    [0023] In one embodiment of the present invention, a first mounting portion for mounting the first evaporator and a second mounting portion for mounting the first condenser may be formed in the first accommodation portion. The first and second mounting portions may be spaced apart along the wall such that a space is formed between the first evaporator and the first condenser.
    [0024] In one embodiment of the present invention, air introduced into the drum may be heated by the first and second heat pump cycles. And the first evaporator and the first condenser can be provided in the first heat pump cycle, and a second evaporator and a second condenser provided in the second heat pump cycle can be arranged between the first and the second mounting portions.
    [0025] In one embodiment of the present invention, an inlet (inlet) and an outlet (outlet) of the flow path can be formed on both sides of the first accommodation portion and at least one evaporator and at least one condenser can be arranged on the two sides. two sides of the first accommodation portion.
    [0026] In one embodiment of the present invention, a plurality of compressor mounting portions may be arranged in the second accommodation portion along the flow path of the first accommodation portion.
    [0027] In one embodiment of the present invention, air introduced into the drum may be heated by the first and second heat pump cycles. The first compressor of the first heat pump cycle may be arranged on one of a plurality of compressor mounting portions and the second compressor of the second heat pump cycle may be arranged on another plurality of compressor mounting portions. At least one of the first and second compressors may be provided with an inverter to change the drive speed of the compressor through a frequency conversion. The first heat pump cycle may be provided with a first evaporator and a first condenser and the second heat pump cycle may be provided with a second evaporator and a second condenser. The first and second heat pump cycles may be arranged such that air introduced into the first accommodation portion passes through the first evaporator, the second evaporator, the second condenser and the first condenser sequentially.
    [0028] In one embodiment of the present invention, a compressor may be arranged in one of the plurality of compressor mounting portions, and no compressor may be arranged in another of the compressor mounting portions such that air introduced into the drum can be heated by a single heat pump cycle.
    [0029] In one embodiment of the present invention, a fan motor for suction of air passing through the flow path may be mounted to the base frame. The motor may be arranged close to the second accommodation portion, in a direction parallel to the first accommodation portion.
    [0030] The present invention may have the following advantages.
    [0031] Firstly, a dehumidifying function and a drying function can be intensified through a heat pump multicycle, and a drying time can be shortened.
    [0032] Second, a heat pump cycle can be driven within a wide range of operating range, by a compressor having an inverter. With such a configuration, even if a peripheral temperature, object quantity, or object's initial moisture content (BMI) amount is outside a specific range, the heat pump cycle can be driven within a reliable compressor range.
    [0033] In addition, a low temperature drying function can be implemented through a multicycle heat pump, and a triggering interval of the low temperature heat pump cycle can be extended through a frequency conversion by the inverter. .
    [0034] Furthermore, a dryer frame, commonly used for a single heat pump cycle and a multicycle heat pump, can be implemented through a base frame having a plurality of accommodation portions.
    [0035] Furthermore, as a flow path is formed by a wall among the plurality of accommodation portions and components are arranged in the flow path, airflow having a small loss can be implemented regardless of the arrangement of the components.
    [0036] Additional scope of applicability of this application will become more evident from the detailed description given below. It should be understood, however, that the detailed description and specific examples, while indicating preferred embodiments of the invention, are provided by way of illustration only, as various changes and modifications within the spirit and scope of the invention will become apparent to those skilled in the art. in the art from the detailed description. BRIEF DESCRIPTION OF THE DRAWINGS
    [0037] The accompanying drawings, which are included to provide a better understanding of the invention and are incorporated into and form a part of this specification, illustrate exemplary embodiments and, together with the description, serve to explain the principles of the invention.
    [0038] In the drawings: FIG. 1 is a schematic view of a garment care apparatus having a heat pump cycle in accordance with an embodiment of the present invention; FIG. 2 is a psychometric graph of air used to perform a drying process in the garment care apparatus of FIG. 1; FIG. 3 is a moliere chart (PH chart) of air used to perform a drying process in the garment care apparatus of FIG. 1; FIG. 4 is a Molière plot (PH plot) comparing a single heat pump cycle with a multicycle heat pump in the case of the same volume of air; FIG. 5 is a flowchart illustrating a control method used for a drying process of the garment care apparatus of FIG. 1; FIG. 6 is a graph illustrating that a high pressure side heat pump cycle reaches a threshold (region of reliable compressor drive); FIGS. 7A to 7C are conceptual views illustrating a control method for a reliable compressor drive region under a first condition in the control method shown in FIG. 5; FIGS. 8A to 8C are conceptual views illustrating a control method for a reliable compressor drive region under a second condition in the control method shown in FIG. 5; FIG. 9 is a graph illustrating a discharge pressure of a compressor having an inverter, relative to a suction pressure when an external load is low; FIG. 10 is a plan view of a base frame provided in the garment care apparatus shown in FIG. 1; FIG. 11 is a sectional view taken along line 'A-A' in FIG. 10; and FIGS. 12 to 14 are conceptual views illustrating that an evaporator, condenser, and compressor are mounted on the base frame of FIG. 10. DETAILED DESCRIPTION OF THE INVENTION
    [0039] The description will now be given in detail of preferred configurations of a garment care apparatus in accordance with the present invention, with reference to the accompanying drawings. For the sake of brief description with reference to the drawings, the same or similar components will be provided with the same or similar reference numerals and description thereof will not be repeated. A singular expression in the specification includes a plural meaning unless it is definitely represented in a contextual way.
    [0040] In embodiments of the present invention, a garment care apparatus is implemented as a condenser-type garment dryer capable of drying an object to be dried, such as damp garments, in an air circulation manner. However, the present invention is not limited thereto. For example, the laundry treatment apparatus of the present invention may be another type of clothes dryer, a washing machine having a drying function, etc.
    [0041] FIG. 1 is a schematic view of a garment care apparatus having a heat pump cycle in accordance with an embodiment of the present invention. FIG. 2 is a psychometric graph of air used to perform a drying process in the garment care apparatus of FIG. 1. FIG. 3 is a moliere chart (PH chart) of air used to perform a drying process in the garment care apparatus of FIG. 1. FIG. 4 is a moliere plot (PH plot) comparing a single heat pump cycle with a multicycle heat pump in the case of the same volume of air.
    [0042] As shown, the garment care apparatus of the present invention includes a housing (not shown), a drum 110, a circulation duct 120, a circulation fan 130, heat pump cycles 140 and 150, and a controller ( not shown).
    [0043] The appearance of garment care apparatus casing forms and a user input unit, a display unit, etc. are provided at an upper end of the housing. A user can select various modes having various functions through the user input unit during the washing process. And the user can check a current status of the garment care apparatus through the display unit.
    [0044] An object to be washed and an object to be dried are accommodated in the drum 110. Therefore, the drum 110 can be referred to as an accommodation chamber. Drum 110 may be cylindrical in shape, having an accommodation space to accommodate an object therein. Drum 110 is rotatably installed in the housing. A front side of the drum 110 is open, and an opening is formed in a front side of the housing. The object can be accommodated in the drum 110 through the opening of the housing and the front side of the drum 110. The drum 110 can be installed in such a way that its axis of rotation can be positioned horizontally in the housing. Drum 110 may be driven by a drive motor installed below the housing. A drive motor output shaft is connected to an outer circumferential surface of drum 110 by a belt. As a rotational force from the drive motor is transmitted to the drum 110 via the belt, the drum 110 can be rotated.
    [0045] The object is dried by heated air circulating through drum 110.
    [0046] The heated air circulates along the circulation duct 120. The circulation duct 120 forms a circulation path such that air can circulate through the drum 110. Since at least part of the circulation duct 120 is communicated with an outlet formed in a front side of the drum 110, air discharged from the outlet of the drum 110 is introduced into the circulation duct 120. Since at least another part of the circulation duct 120 is communicated with an inlet formed in a rear side from the drum 110, air inside the circulation duct 120 is supplied to the inlet of the drum 110.
    [0047] The air inside the circulation duct 120 moves along the circulation duct 120, upon receiving a circulation driving force from the circulation fan 130. One or more circulation fans 130 can be installed in the circulation duct. 120, and air within circulation duct 120 is introduced into drum 110 as circulation fan 130 is operated. Air passing through drum 110 moves along circulation duct 120 and is introduced into the inlet of drum 110 in a circulating fashion. The circulating fan 130 is connected to the drive motor and can be driven by receiving a drive force from the drive motor.
    [0048] As shown, the circulating air is heated by a plurality of heat pump cycles. The plurality of heat pump cycles include a first heat pump cycle 140 and a second heat pump cycle 150. However, the present invention is not limited thereto. For example, more than 3 heat pump cycles can be provided to perform a control of the present invention to be explained later.
    [0049] The first and second heat pump cycles 140 and 150 absorb heat from a low temperature region and radiate the absorbed heat to a high temperature region, thereby transferring heat from the low temperature region to the high temperature region. high temperature. In this case, the circulating air is heated in the high temperature region.
    [0050] More specifically, the first heat pump cycle 140 includes a first evaporator 141, a first compressor 143, a first condenser 142, and a first expansion valve 144.
    [0051] The first evaporator 141 can be arranged in the low temperature region to absorb heat, and the first condenser 142 can be arranged in the high temperature region to radiate heat. For example, the first evaporator 141 can be installed in the circulation duct 120 connected to the outlet of the drum 110. And the first condenser 142 can be installed in the circulation duct 120 connected to the inlet of the drum 110. The first evaporator 141 and the first condenser 142 are spaced apart in the circulation duct 120. Based on an airflow direction, the first evaporator 141 can be installed on an upstream side of the circulation duct 120 and the first condenser 142 can be installed on an upstream side. downstream of the circulation duct 120.
    [0052] A moving path of heated air along circulation duct 120 will be explained. Once circulation fan 130 is operated, dry air heated within circulation duct 120 is introduced into the inlet of drum 110 to dry clothing (an object) accommodated in drum 110. Then, air is discharged from drum 110. Moist air discharged from drum 110 passes through first evaporator 141 and is then reintroduced into drum 110 via first condenser 142. In this case, air discharged from drum 110 (e.g., air having a temperature of about 40°C ) has its heat removed from the first evaporator 141 and is heated in the first condenser 142. Then, air is introduced into the drum 110. The air passing through the drum 110 is cooled, condensed and dehumidified by the first evaporator 141. And the air passing through of the first evaporator 141 is heated by the first condenser 142.
    [0053] The first evaporator 141 can be configured as various types including a board type, a printed circuit board type, a finned tube type, etc. The first evaporator 141 shown in FIG. 2 is configured as a finned tube type.
    [0054] A finned tube type heat exchanger may be composed of a plurality of heat exchange fins formed as a plate type and a plurality of heat exchange tubes penetrating the heat exchange fins in one direction horizontal. The plurality of heat exchange tubes can be connected together by a connecting tube bent into a semi-circular shape, and an operating fluid can flow in the heat exchange tubes. The heat exchange fins may be arranged in the circulation duct 120 in a vertical direction and may be spaced from each other in a direction crossing an airflow direction. With such a configuration, air discharged from drum 110 contacts the heat exchange fins and heat exchange tubes as it passes through an air passage between the heat exchange fins. Therefore, the operating fluid exchanged heat with the air. The heat exchange fins are connected to the heat exchange tubes so as to increase the contact area between the heat exchange tubes and air. In this specification, an operating fluid may be referred to as a refrigerant fluid.
    [0055] As mentioned above, the first condenser 142 may be a finned tube type heat exchanger, and detailed explanations thereof will be omitted. Heat from air passing through drum 110 is transferred to be absorbed by a refrigerant fluid from the first evaporator 141, and heat from a refrigerant fluid from the first condenser 142 is transferred to radiate air passing through the first evaporator 141.
    [0056] The first evaporator 141, the first condenser 142 and the first expansion valve 144 are connected together by a first flow tube 145. The first flow pipe 145 forms a closed loop.
    [0057] A moving path of a refrigerant fluid flowing in the first circulation tube 145 will be explained. The refrigerant fluid passes through the first evaporator 141, the first compressor 143, the first condenser 142 and the first expansion valve 144. Then, the refrigerant fluid is reintroduced into the first evaporator 141.
    [0058] The first evaporator 141 absorbs heat from the air passing through the drum 110 and transfers the absorbed heat to a refrigerant fluid from the heat exchange tubes. Therefore, a low-temperature, low-pressure liquid refrigerant introduced into the first evaporator 141 is converted into a low-temperature, low-pressure gaseous refrigerant. Air passing through the evaporator is cooled by the latent heat of gasification due to a change in state of the refrigerant in the first evaporator 141, thereby being condensed and dehydrated.
    [0059] Low temperature, low pressure gaseous refrigerant, discharged from the first evaporator 141, flows along the first circulation tube 145 and is introduced into the first compressor 143.
    [0060] The first compressor 143 is configured to compress a low temperature, low pressure gaseous refrigerant and to form a high temperature, high pressure gaseous refrigerant. Therefore, it is possible to radiate the heat absorbed in the low temperature region from the high temperature region.
    [0061] High temperature, high pressure gaseous refrigerant, discharged high from the first compressor 143, flows along the first circulation tube 145 and is introduced into the first condenser 142.
    [0062] As the first condenser 142 transfers and radiates heat from the high temperature, high pressure gaseous refrigerant to the air discharged from the first evaporator 141, the high temperature, high pressure gaseous refrigerant is converted into a liquid refrigerant of high temperature and high pressure. Latent heat of condensation, due to a change in state of the refrigerant fluid in the first condenser 142, can be used to heat the air passing through the first condenser 142.
    [0063] The high temperature, high pressure liquid refrigerant, discharged from the first condenser 142, flows along the first circulation tube 145 and is introduced into the first expansion valve.
    [0064] The first expansion valve 144 is configured to expand a high temperature, high pressure liquid refrigerant and to form a low temperature, low pressure liquid refrigerant. It is therefore possible to absorb heat from the air passing through the drum 110.
    [0065] The low-temperature, low-pressure liquid refrigerant, discharged from the first expansion valve 144, flows along the first circulation tube 145 and is reintroduced into the first evaporator 141. In this case, the low-pressure liquid refrigerant temperature and low pressure can be partially converted to a low temperature, low pressure, gaseous refrigerant by moving along the first circulation tube 145. Therefore, a low temperature, low pressure refrigerant, introduced into the first evaporator 141 , can be in a mixed state between a gaseous state and a liquid state.
    [0066] A different type of evaporator and condenser may be provided between the first evaporator 141 and the first condenser 142. For example, the second heat pump cycle 150 is provided with a second evaporator 151, a second compressor 153, a second condenser 152 and a second expansion valve 154. The second evaporator 151 and the second condenser 152 are arranged in such a way that air introduced into the accommodation chamber can pass through the first evaporator 141, the second evaporator 151, the second condenser 152 and the first capacitor 142, sequentially.
    [0067] In this case, the second evaporator 151, the second compressor 153, the second condenser 152 and the second expansion valve 154 have the same functions as the first evaporator 141, the first compressor 143, the first condenser 142 and the first valve expansion module 144 and thus its detailed explanation will be omitted.
    [0068] A second cycle coolant of heat pump 150 may be the same as or different from that of first cycle of heat pump 140. If the coolant of second cycle of heat pump 150 is different from that of first cycle of heat pump 140, the First and second heat pump cycle refrigerants can be straight-type refrigerants with consideration of temperature, pressure, a high latent heat ratio, price, etc.
    [0069] The second evaporator 151, the second compressor 153, the second condenser 152 and the second expansion valve 154 are connected together by a second circulation tube 155 and the second circulation tube 155 forms a closed loop. With such a configuration, the second evaporator 151 removes moisture from circulating air, and the second condenser 152 heats air introduced into the drum 110.
    [0070] An operation of the first and second heat pump cycles 140 and 150 is controlled by the controller and each of the first and second heat pump cycles 140 and 150 is operated as an independent heat pump multicycle. Therefore, wet steam, evaporated from an object to be washed and to be dried inside the drum 110, is dehumidified through the first and second evaporators 141 and 151. During this process, sensible heat and latent heat collected from the first and the second evaporators 141 and 151 are converted to high temperature, high pressure heat by the first and second compressors 143 and 153. Then, the heat is radiated through the first and second condensers 142 and 152 and is used to dry the object inside drum 110. In this case, the first heat pump cycle 140 can be a high pressure side cycle, and the second heat pump cycle 150 can be a low pressure side cycle.
    [0071] More specifically, as shown, wet steam evaporated from the drum first contacts the evaporator of the first heat pump cycle 140, an external independent cycle, before contacting the evaporator of the second heat pump cycle thermal 150, an internal independent cycle. During such a dehumidification process, an enthalpy of the wet steam is reduced. Moist steam devoid of sensible heat and latent heat has its temperature-humidity reduced and requires a low evaporation temperature for more effective dehumidification. The wet steam increases an hourly amount of dehumidification as it passes through the second evaporator 151 of the second heat pump cycle 150, the second evaporator 151 having a relatively lower evaporation temperature. Consequently, wet steam is in a state to reduce drying time.
    [0072] The second evaporator 151 has a lower evaporating pressure (evaporating temperature) than the first evaporator 141 having a relatively higher pressure. The reason is because the enthalpy of wet steam passing through the first evaporator 141 is reduced. As a result, a condensing pressure (condensation temperature) is reduced. Air, which was first heated through second condenser 152, is heated to a higher temperature through first condenser 142 having a relatively higher condensing pressure (condensing temperature). When compared with a single heat pump cycle, in the multicycle heat pump, evaporation efficiency is more intensified as air passing through two evaporators has a large amount of dehumidification and as drier air is introduced into the drum after being heated to a high temperature.
    [0073] Referring to FIG. 2, Moist air in a dry state (A), introduced into the drum through the condenser, has low temperature and high humidity through a constant enthalpy change when it reaches a dry steady state. In the low-temperature, high-humidity state (B), moist air is discharged from the drum outlet. When compared to the single heat pump cycle indicated by the dotted line, the multicycle heat pump indicated by the solid line can cause a higher cooling capacity with respect to the same inlet as shown in formula 1 below, and a more intensified dehumidification capacity , as shown in formula 2 below. As a result, not only drying energy but also drying time can be reduced. [Formula 1]
    Where,
    Dry air mass flow [Formula 2]

    [0074] FIG. 3 is a graph comparing a side refrigerant from the first heat pump cycle 140 to that from the second heat pump cycle 150. The dotted line indicates a moliere graph (PH graph) when a drying time is shortened by increasing a capacity maximum cooling capacity by increasing compressor capacity, in a single heat pump cycle. Referring to FIG. 3, a compressor discharge pressure is increased as a cooling capacity is increased to the maximum, and drive efficiency is drastically reduced as a pressure ratio is increased. On the other hand, the heat pump multicycle is independently driven by two evaporating temperatures and two condensing temperatures. The evaporator is configured such that a low pressure evaporator subsequent to a high pressure evaporator has a lower temperature than a single heat pump cycle for effective dehumidification. Also, in the evaporator, a cycle is split to reduce a pressure ratio of each compressor and to increase the coefficient of performance. This can result in a short drying time and a high-efficiency drive.
    [0075] In this case, once the drastic rise of a discharge temperature on one discharge side of the compressor is prevented, the compressor can have high reliability. And the compressor can be driven with a margin with respect to a motor winding temperature limiting line due to the increase in discharge temperature.
    [0076] For similar cooling capacity, a compression ratio can be formed to be higher on the single heat pump cycle, but be very small on a lower pressure side (second heat pump cycle) of the heat pump multicycle. The higher the compression ratio is, the lower the efficiency of the compressor. Therefore, it is preferable to run the cycles by properly divided compression ratios, for low energy consumption with an increased cooling capacity (a reduced drying time).
    [0077] Referring to FIG. 4, on an assumption that the drying performance is similar under the same volume of air as an operating fluid, a high pressure side and a low pressure side of a system having the heat pump multicycle are shown in a region lower of the PH graph than that of a system having the single heat pump cycle. As a result, air temperature within a closed flow path system of the garment care apparatus is reduced. This results in a decrease in temperature of dry air introduced into the drum after being heated through the condenser. Therefore, an object to be dried is dried at a lower temperature than in the single heat pump cycle.
    [0078] As shown, reducing pressure of a refrigerant fluid on the evaporator side of the single heat pump cycle is greater than that on the evaporator side of the multicycle heat pump. This results in a large amount of refrigerant flowing in a single evaporator. If the heat pump multicycle is independently driven, a refrigerant fluid flows at each cycle in a divergent manner. This can reduce the amount of refrigerant circulation per cycle, thereby reducing a pressure loss of a refrigerant on the evaporator side. This is related to an increase in cooling capacity, which is advantageous in maintaining a high compressor suction pressure and reducing the compression ratio.
    [0079] More specifically, in the case of the single heat pump cycle, air introduced at the inlet of the drum through the condenser having a condensing temperature of about 84°C has a temperature greater than 80°C. On the other hand, in the case of the heat pump multicycle, air introduced into the drum inlet through the low pressure side condenser (condensation temperature: 47°C) and the high pressure side condenser (condensation temperature: approx. C) has a temperature below 66°C. In both cases, the difference between the air temperatures is about 15°C. This can cause a difference in clothing damage.
    [0080] As shown in FIG. 2, a psychometric graph of a multicycle heat pump is skewed more to the lower left than that of a single heat pump cycle. Since a change in dw (absolute humidity difference) or a change in Qe (cooling capacity index) rarely occurs, a drying time can be the same. If necessary, the degree of clothing damage due to temperature and friction can be determined in a synthesized way, by increasing the cooling capacity by narrowing the temperature difference of 15°C (t3-t'3), by decreasing a temperature at an appropriate level and by shortening the drying time.
    [0081] Furthermore, the garment care apparatus according to the present invention is provided with an inverter (not shown) configured to change a drive speed of the first compressor 143 and the second compressor 153 through a frequency conversion or a frequency change. In this case, the controller controls a drive speed of at least one of the first compressor 143 and the second compressor 153 using the inverter, thereby operating at least one of the first compressor 143 and the second compressor 153 within a range of default trigger. With such a configuration, the garment treatment apparatus according to the present invention can maintain cycles within an operating region despite a change in a peripheral temperature, the amount of the object (drying load) or the amount of content. initial moisture content (BMI) of the object. In the following, such structure and function will be explained in more detail with reference to FIGS. 5 to 9.
    [0082] FIG. 5 is a flowchart illustrating a control method used for a drying process of the garment care apparatus of FIG. 1. FIG. 6 is a graph illustrating that a high-pressure side heat pump cycle reaches a limiting point (region of reliable compressor drive). FIGS. 7A to 7C are conceptual views illustrating a control method for a reliable compressor drive region under a first condition in the control method shown in FIG. 5. FIGS. 8A to 8C are conceptual views illustrating a control method for a reliable compressor drive region under a second condition in the control method shown in FIG. 5. FIG. 9 is a graph illustrating a discharge pressure of a compressor having an inverter, relative to a suction pressure when an external load is low.
    [0083] Referring to FIG. 5, a control method used for a drying process of the garment treatment apparatus includes the first heat pump cycle 140, the second heat pump cycle 150 and the circulating fan 130 (refer to FIG. 1) for drying an object (S110).
    [0084] In this case, circulating air, passing through the drum 110, circulates in the circulation duct by the circulation fan. Then, the circulating air passes through the first evaporator 141, the second evaporator 151, the second condenser 152 and the first condenser 142. The circulating air is cooled by being stripped of heat by the first and second evaporators 141 and 152. Then , the cooled air is heated as it passes through the second condenser 152 and the first condenser 142.
    [0085] Before the drying process, a process of preheating the drum 110, the circulation duct 120, etc. can be performed. using only a heating effect of at least one of the first and second condensers 142 and 152. For example, in order to effectively use the heat discharged from at least one of the first and second condensers 142 and 152, air discharged from the drum 110 during a washing process and a dehydration process may bypass the first and second evaporators 141 and 151 to thereby be introduced into at least one of the first and second condensers 142 and 152. As air passes through of the drum 110 is introduced into at least one of the first and second condensers 142 and 152 to thereby be heated, without being cooled by the first and second evaporators 141 and 151, a heating effect of the condenser can be maximized. In order to use one of the first and second capacitors 142 and 152, or both of the first and second capacitors 142 and 152 during a preheat process, one of the first and second heat pump cycles may be driven. , or both of the first and second heat pump cycles can be triggered.
    [0086] Referring again to FIG. 5, after the first heat pump cycle 140, the second heat pump cycle 150 and the circulating fan 130 are turned on, a peripheral temperature, the quantity of the object or the amount of initial moisture content (BMI) of the object is determined by a sensor mounted to a predefined part (S120).
    [0087] For example, the sensor may be a temperature sensor provided in at least one of the first and second heat pump cycles. The controller determines a peripheral temperature, the amount of the object, or the amount of initial moisture content (BMI) of the object, based on a temperature measured by the temperature sensor. The temperature measured by the temperature sensor can be a condensing temperature of the condenser or a discharge temperature of the compressor, for example. More specifically, the controller detects, using the sensor, if one of the condensing temperatures between the first and second condensers is outside a predefined range, or if one of the discharge temperatures of the first and second compressors is outside a predefined range. .
    [0088] In this case, if the condensing temperature of the condenser or the discharge temperature of the compressor is outside a predefined range, the controller can determine that at least one of a peripheral temperature, the quantity of the object and the quantity of content of Initial humidity (BMI) of the object is outside a specific range.
    [0089] For example, when a peripheral temperature is higher than a preset temperature, when the quantity of the object is greater than a preset amount, or when the amount of initial moisture content (BMI) of the object is greater than a preset amount, the 140 first heat pump cycle, a high pressure side heat pump cycle hits a limiting point at a fast speed. In this case, the condensing temperature of the first condenser 142 or the discharge temperature of the first compressor 143 is outside a predefined range. In this way, the controller detects if at least one of a peripheral temperature, the quantity of the object and the amount of initial moisture content (BMI) of the object is outside an upper limit value within a predefined range using the condensing temperature. of the first condenser 142 or the discharge temperature of the first compressor 143.
    [0090] On the contrary, when a peripheral temperature is lower than a preset temperature, when the object quantity is lower than a preset amount, or when the object's initial moisture content (BMI) amount is less than a preset amount , both the first heat pump cycle 140 and the second heat pump cycle 150 are stunted. Such growth retardation can also be detected based on the condensing temperature of the condenser or the discharge temperature of the compressor. Condenser condensing temperature or compressor discharge temperature, which causes cycle growth retardation, can be set to a specific value or a specific range through experiments.
    [0091] As another example, if a peripheral temperature is high or low it can be detected by the temperature sensor before the first heat pump cycle 140, the second heat pump cycle 150 and the circulating fan 130 are driven. In this case, the trigger step (S110) is omitted. In the determining step (S120), the degree of peripheral temperature is determined before the first heat pump cycle 140, the second heat pump cycle 150 and the circulation fan 130 are driven.
    [0092] As yet another example, if the object quantity is greater or less than a predefined quantity it can be detected before the first heat pump cycle 140, second heat pump cycle 150 and circulation fan 130 are triggered. Once the amount of the object inside the drum is measured by a weight sensor, etc., the trigger step (S110) is omitted. And in the determining step (S120), the degree of the quantity of the object is determined before the first heat pump cycle 140, the second heat pump cycle 150 and the circulating fan 130 are driven.
    [0093] As shown, after the determination step (S120), the compressor can be controlled (S130). For example, when at least one of a peripheral temperature, object quantity, and object's initial moisture content (BMI) amount is outside a specific range, the controller controls a drive speed within at least one tooth the first compressor 143 and the second compressor 153 (refer to FIG. 1) (S130).
    [0094] By controlling the drive speed, at least one of the first compressor 143 and the second compressor 153 can be provided with an inverter to change the drive speed of the compressor through a frequency conversion. The controller drives at least one of the first compressor and the second compressor within a predefined drive range by controlling a drive speed of at least one of the first and second compressors. In this case, the preset trigger range indicates a compression ratio range, and the second compressor can be formed to have a higher compression ratio than the first compressor.
    [0095] More specifically, referring to FIGS. 6 to 9, at least one of the first compressor and the second compressor can be driven in a first mode where the drive speed is constant as a first speed and a second mode where the drive speed is varied from the first speed to a second speed. velocity. The constant drive speed corresponding to the first speed is transformed into another speed corresponding to the second speed. In this case, when at least one of a peripheral temperature, the quantity of the object and the amount of initial moisture content (BMI) of the object is outside a specific range, the controller controls at least one of the first compressor and the second compressor. to be activated in the second mode.
    [0096] As mentioned above, the peripheral temperature, the object quantity, or the object's initial moisture content (IMC) amount is determined based on a condenser condensing temperature or a compressor discharge temperature detected by at least one of the first and second heat pump cycles. In this way, the controller controls a drive speed of at least one of the first and second compressors, based on the detected condensing temperature or the detected discharge temperature. As mentioned above, if the peripheral temperature or quantity of the object is determined by a temperature sensor or a weight sensor, a drive speed of at least one of the first and second compressors can be controlled based on a value of detection by the temperature sensor or the weight sensor.
    [0097] As an example for controlling the drive speed, a drive frequency of the inverter can be controlled to be reduced at a specific time when at least one of the peripheral temperature, the object quantity and the amount of initial moisture content (BMI) of the object is greater than an upper threshold value or lower than a lower threshold value within the specified range.
    [0098] As mentioned above, when the peripheral temperature is higher than a preset value, when the object quantity is higher than a preset amount, or when the object's initial moisture content (BMI) amount is higher than a preset amount, as shown in FIG. 6, the first heat pump cycle 140, a high pressure side heat pump cycle hits a limiting point (a reliable compressor drive region) at a fast speed.
    [0099] In this case, the high pressure side heat pump cycle or low pressure side heat pump cycle must be kept within an operating range when shutting down and then re-operating. While the heat pump cycle is off, a loss of cooling capacity is caused. This can result in increased drying time and increased energy cost (in terms of energy consumption of a motor to drive the circulating fan and drum). More specifically, in order to safely perform an initial start of the compressor that has been turned off, a waiting time of about 3 minutes is required. Waiting time can damage the appearance of a drying time. In this embodiment, since at least one of a high pressure side heat pump cycle and a low pressure side heat pump cycle is provided with an inverter, the high pressure side heat pump cycle and the low pressure side heat pump cycle can be moved to a reliable compressor drive region as a drive frequency of at least one compressor changes. With such a configuration, the compressor can run for a long time and can be run continuously without turning off the cycle. This can allow the compressor to maintain its performance in a protected state and can minimize drying time.
    [00100] In a first condition where at least one of a peripheral temperature, the quantity of the object and the amount of initial moisture content (BMI) of the object is greater than an upper limit value within the specified range, the first and the second second compressors have the same drive speed in the first mode. However, in the second mode, one of the first and second compressors that has an inverter may have a reduced drive speed.
    [00101] Referring to FIG. 7A, in a case where each of the first and second compressors is provided with an inverter, each of the first and second compressors is driven in the first mode at a constant speed. Then, if it is determined that at least one of the peripheral temperature, the quantity of the object and the amount of initial moisture content (BMI) of the object is outside a specific range, the drive speed of the first and second compressors is reduced. to run the second mode. In this case, the first compressor is indicated as a dotted line, and the second compressor is indicated as a solid line.
    [00102] However, the present invention is not limited thereto. For example, if it is determined that at least one of the peripheral temperature, the amount of the object, and the amount of initial moisture content (BMI) of the object is outside a specific range in the first mode, the trigger speed of only one of the first and second compressors can be reduced.
    [00103] As another example, a drive frequency of the second compressor, the low pressure side compressor can be reduced to an operable size, and then the drive speed of the first compressor, the high pressure side compressor can be controlled. On the contrary, a drive frequency of the first compressor, the high pressure side compressor can be reduced to an operable size, and then the drive speed of the second compressor, the low pressure side compressor can be controlled.
    [00104] Referring to FIG. 7B, in a case where the first compressor is provided with an inverter and the second compressor is driven at a constant speed, drive of the compressors can be controlled within a reliable region by reducing the drive speed of the first compressor. Referring to FIG. 7C, in a case where the second compressor is provided with an inverter and the first compressor is driven at a constant speed, drive of the compressors can be controlled within a reliable region by decreasing the drive speed of the second compressor.
    [00105] As mentioned above, in the present invention, at least one of the first and second compressors can be driven in the first mode where the drive speed is constant, and in the second mode where the constant drive speed is changed to another speed. . In this case, if at least one of the peripheral temperature, the amount of the object and the amount of initial moisture content (BMI) of the object is outside a specific range, the controller starts at least one of the first and second compressors on the second way.
    [00106] Such a triggering method can also be applicable in a second condition where a peripheral temperature is lower than a preset temperature, the object quantity is lower than a preset quantity or when the initial moisture content (BMI) quantity of the object is less than a preset amount.
    [00107] In the case of the second condition, as mentioned above, it takes a long time to reach a constant rate drying section (region), since both the high pressure side heat pump cycle and the side heat pump cycle low pressure have growth retardation. This may result from a feature of a dryer having a heat pump cycle, a different type of dryer from an electric heater to provide a constant amount of heat at all times. This occurs when the periphery or a drying load has a low enthalpy.
    [00108] In this case, as shown in FIGS. 8A to 8C, the controller drives at least one of the first and second compressors in the second mode.
    [00109] For example, as shown in FIG. 8A, in a case where each of the first and second compressors is provided with an inverter, each of the first and second compressors can be driven at a high speed in the first mode, thereby accelerating cycle growth and inducing a region of high temperature and high humidity (moving to the upper right region on the psychrometric plot) where cycle efficiency is increased. With such a configuration, the drive efficiency is intensified and a drying time is shortened. The controller then executes the second mode by reducing the drive speed between the first and second compressors. In the second condition, an auxiliary heat source, such as a heater, can be provided for growing cycles.
    [00110] As another example, referring to FIG. 8B , in a case where the first compressor is provided with an inverter and the second compressor is driven at a constant speed, the first compressor, the high pressure side compressor may initially be driven at a high speed. Then, the drive speed of the first compressor can be reduced, thereby accelerating cycle growth. As yet another example, referring to FIG. 8C, in a case where the second compressor is provided with an inverter and the first compressor is driven at a constant speed, the second compressor, the low pressure side compressor may initially be driven at a high speed. Then, the drive speed of the second compressor can be reduced, thereby accelerating cycle growth.
    [00111] Referring to FIG. 9, when an external load is small, a compressor having an inverter and driven at a high speed increases a drum inlet side air temperature (temperature is proportional to the amount of heat) higher than a constant speed compressor. When compared to a pressure change from a constant speed compressor indicated by the solid line, a pressure change from a high speed compressor indicated by the dotted line implements a high pressure discharge and a high pressure ratio and makes the cycles quickly reach a constant rate drying section.
    [00112] Referring again to FIG. 5, after the drive speed is changed, the first and second compressors are driven at a constant speed until a drying process is completed (S140).
    [00113] That is, at least one of the first and second compressors can be driven in the first and second modes and then can be driven in a third mode where the drive speed is maintained as the second speed.
    [00114] According to such a control method, bad influences on clothing due to a high temperature can be entirely reduced by a low temperature drying operation. In the case of an underwear course that is more sensitive to a temperature, etc., one of the high pressure side cycle and the low pressure side cycle is driven at a lower speed, in a state where the garment rarely has moisture left in it. a final drying stage. As the controller induces a reduced temperature, a state of an object to be dried can be intensified. Furthermore, as the drive speed of the compressor having an inverter is more controlled, a low temperature drive region can be further extended.
    [00115] The garment treatment apparatus of the present invention can be selectively provided with the first and second heat pump cycles. For example, garment care apparatus having a single heat pump cycle is provided with a mechanism to easily change the single heat pump cycle into a multi cycle heat pump according to a selection of the designer or user. In the following, such a mechanism will be explained in more detail with reference to the attached drawings.
    [00116] FIG. 10 is a plan view of a base frame provided in the garment care apparatus shown in FIG. 1 and FIG. 11 is a sectional view taken along line 'A-A' in FIG. 10. FIGS. 12 to 14 are conceptual views illustrating that an evaporator, condenser, and compressor are mounted on the base frame of FIG. 10.
    [00117] Referring to the drawings, the garment care apparatus is provided with a base frame 160 and at least one evaporator 141 and 151, at least one condenser 142 and 152 and at least one compressor 143 and 153 are mounted on the base frame 160. More specifically, single heat pump cycle components, or multicycle heat pump components may be mounted on base frame 160. As mentioned above, the at least one condenser 142 and 152 heats air introduced into the base frame 160. drum and the at least one compressor is combined with the at least one condenser 142 and 152 and the at least one evaporator 141 and 151 to form a heat pump cycle.
    [00118] For example, at least part of first heat pump cycle components 140 and at least part of second heat pump cycle components 150 (refer to FIG. 1) may be mounted together in base frame 160. In this case, components of the heat pump multicycle are mounted on the base frame 160. As another example, the components of the second heat pump cycle 150 cannot be mounted on the base frame 160, but only the components of the single heat pump cycle can be mounted on the base frame 160.
    [00119] The base frame 160 can be applied to either a single heat pump cycle or a multicycle heat pump. That is, a heat exchanger module and a compressor package module are inserted into the base frame 160 according to each scenario for cost and production efficiency.
    [00120] Base frame 160 may have modules inserted into it for common use and may have a flow path. For example, the base frame 160 is provided with a first accommodation portion 161, a second accommodation portion 162 and a wall or barrier 163. The wall may be one of a side wall, a dividing wall or a boundary wall.
    [00121] The first accommodation portion 161 is configured to accommodate the at least one evaporator 141 and 151 and the at least one condenser 142 and 152 therein. The first accommodation portion 161 may be formed elongated in one direction so as to extend along a direction of flow of air introduced into the drum. As a surface of the first accommodation portion 161 is recessed, side walls can be formed at two ends and two edges. The two ends can be an air inlet and an air outlet. For example, an inlet 161a, through which air is introduced into the first accommodation portion 161, and an outlet 161b, through which air passing through the first accommodation portion 161 to a nozzle portion 164 can be formed at both ends. of the first accommodation portion 161. The inlet 161a and the outlet 161b may be an inlet and an outlet of the flow path which are formed on two sides of the first accommodation portion.
    [00122] The second accommodation portion 162 is configured to accommodate the at least one compressor 143 and 153 therein and is arranged in parallel with the first accommodation portion 161. The second accommodation portion 162 may extend in a direction parallel to said direction. A plurality of compressor mounting portions 162a and 162b may be arranged in the second accommodation portion 162 along the flow path of the first accommodation portion 161.
    [00123] The wall 163 can be formed to divide the first and second accommodation portions 161 and 162 from one another such that the flow path can be formed in the first accommodation portion 161. In this way, the partition 163 forms a side wall of the first accommodation portion 161 and a side wall of the second accommodation portion 162.
    [00124] More specifically, the first accommodation portion 161 will be explained again. A first mounting portion 161c for mounting the first evaporator 141 and a second mounting portion 161d for mounting the first condenser 142 may be formed on the first accommodation portion 161. Since the first evaporator 141 and the first condenser 142 are included in the first heat pump cycle 140, the components of the first heat pump cycle 140 may be mounted on the first and second mounting portions 161c and 161d. In this way, the at least one evaporator and the at least one condenser are arranged on two sides of the first accommodation portion 161 and the laundry apparatus is provided with a single heat pump cycle, as shown in FIG. 13.
    [00125] In this case, a compressor can be provided in only one of the plurality of compressor mounting portions 162a and 162b, such that air introduced into the drum can be heated by a single heat pump cycle. More specifically, the first compressor 143 is mounted to one of a plurality of compressor mounting portions 162a and 162b, and another compressor mounting portion is maintained as a void.
    [00126] As another example, the second heat pump cycle components 150 may be arranged between the first and second mounting portions 161c and 161d. In this case, as shown in FIG. 12, air introduced into the drum can be heated by the first and second heat pump cycles 140 and 150.
    [00127] Referring to FIGS. 10, 11 and 12, the second evaporator 151 and the second condenser 152 provided in the second heat pump cycle 150 may be arranged between the first and second mounting portions 161c and 161d. For this, the first and second mounting portions 161c and 161d are spaced apart along the wall 163 such that a space can be formed between the first evaporator 141 and the first condenser 142, and the second evaporator 151 and the second capacitor 152 are arranged in space. With such a structure, the first and second heat pump cycles 140 and 150 can be arranged such that air introduced into the first accommodation portion 161 can pass through the first evaporator 141, the second evaporator 151, the second condenser 152 and the first capacitor 142, sequentially.
    [00128] As shown, the first compressor 143 of the first heat pump cycle 140 may be arranged in one of a plurality of compressor mounting portions 162a and 162b and the second compressor 153 of the second heat pump cycle 150 may be arranged in another compressor mounting portion. In this case, at least one of the first and second compressors 143 and 153 is provided with an inverter for varying the drive speed of the compressor through a frequency conversion. With such a configuration, the features mentioned above, with reference to FIGS. 1 to 10, can be implemented.
    [00129] Referring to the drawings, a motor 131 of a fan, configured to suck air passing through the flow path, can be mounted on the base frame 160. The fan can be the circulation fan 130 (refers to the Fig. 1), and the motor 131 of the circulating fan 130 can be mounted on the base frame 160 for support. In this case, the motor 131 can be arranged close to the second accommodation portion 162, in a direction parallel to the first accommodation portion 161. With such a structure, the circulating fan 130 can be integrated with the components of the first and second cycles of operation. heat pump 140 and 150 through the base frame 160.
    [00130] As another example, as shown in FIGS. 11 and 13, compressors 143 and 173 having different capacities can be selectively mounted to the base frame 160 in a single heat pump cycle. More specifically, the third compressor 173 having a capacity greater than the first compressor 143 may be mounted to one of a plurality of compressor mounting portions 162a and 162b. And a third evaporator 171 having a capacity greater than the first evaporator 141 and a third condenser 172 having a capacity greater than the first condenser 142 can be mounted on the first accommodation portion 161. In this case, parts of the third evaporator 171 and the third condenser 172, which are increased from the first evaporator 141 and the first condenser 142 by volume, may be arranged between the first and second mounting portions 161c and 161d of the first accommodation portion 161.
    [00131] With such a structure, a single heat pump cycle of a different capacity can be selectively mounted on the base frame.
    [00132] The garment care apparatus having the base frame according to the present invention may be cycled by a combination of the examples mentioned above. Such a combination can be variously implemented according to a compressor capacity, the number of heat exchangers or a variable such as a capacity, according to whether an inverter is provided or not, etc.
    [00133] As the present features can be modalized in various ways without departing from their characteristics, it should also be understood that the modalities described above are not limited by any of the details of the above description, unless otherwise specified, but , rather, is to be broadly interpreted within its scope defined in the appended claims, and therefore all changes and modifications that are within the claims' described limits, or equivalents of such described limits, are therefore intended to be understood. by the attached claims. List of Examples of the Invention
    [00134] Example 1. A garment care apparatus comprising: an accommodation chamber 110, in which an object is accommodated; a first heat pump cycle 140 having a first evaporator 141, a first compressor 143, a first condenser 142 and a first expansion valve 144; a second heat pump cycle 150 having a second evaporator 151, a second compressor 153, a second condenser 152 and a second expansion valve 154, and arranged such that air introduced into the accommodation chamber 110 passes through the first evaporator 141, the second evaporator 151, the second condenser 152 and the first condenser 142, sequentially; and a controller configured to control an operation of the first and second cycles of the heat pump 140 and 150, wherein at least one of the first and second compressors 143 and 153 is provided with an inverter for changing the drive speed of the compressor through a frequency conversion, and wherein the controller drives at least one of the first compressor 143 and the second compressor 153 within a predefined drive range by controlling the drive speed of at least one of the first and second compressors compressors 143 and 153 using the inverter.
    [00135] Example 2 The garment treatment apparatus according to example 1, wherein at least one of the first compressor 143 and the second compressor 153 is driven in a first mode where the drive speed is constant as a first speed and a second mode where the drive speed is varied from the first speed to a second speed.
    [00136] Example 3 The garment care apparatus according to example 2, wherein when at least one of a peripheral temperature, an object quantity and an object's BMI initial moisture content quantity is outside a range specific, the controller controls at least one of the first compressor 143 and the second compressor 153 to be driven in the second mode.
    [00137] Example 4 The garment care apparatus according to example 3, wherein an inverter drive frequency is controlled to be reduced at a specific time when at least one of the peripheral temperature, the amount of the object and the amount of the object's BMI initial moisture content is greater than an upper limit value or lower than a lower limit value of the specific range.
    [00138] Example 5 The garment care apparatus according to example 3 or 4, wherein in a case where at least one of the peripheral temperature, the quantity of the object and the amount of initial moisture content BMI of the object is greater than an upper limit value of the specified range, the first and second compressors 143 and 153 have the same drive speed in the first mode, and one of the first and second compressors 143 and 153 that has the inverter has its speed reduced actuation in the second mode.
    [00139] Example 6 The laundry treatment apparatus according to any one of examples 2 to 5, wherein at least one of the first and second compressors 143 and 153 is driven in the first and second modes and then is driven in a third mode where the drive speed is maintained as the second speed.
    [00140] Example 7 The laundry treatment apparatus according to any one of examples 1 to 6, wherein the controller controls the drive speed of at least one of the first and second compressors 143 and 153, based on a condensing temperature of condenser 142 and 152 or a discharge temperature of compressor 143 and 153, the temperature detected in at least one of the first and second heat pump cycles 140 and 150.
    [00141] Example 8 The laundry treatment apparatus according to example 7, wherein if the condensing temperature of condenser 142 and 152 or the discharge temperature of compressor 143 and 153 is outside a predefined range, the controller determines that at least one of a peripheral temperature, object quantity, and object's BMI initial moisture content amount is outside a specific range.
    [00142] Example 9 The garment care apparatus according to any one of Examples 1 to 8, wherein the preset drive range indicates a compression ratio range, and the second compressor 153 is formed to have a compression ratio. higher compression than the first compressor 143.
    [00143] Example 10 The laundry treatment apparatus according to example 9, wherein the second compressor 153 is provided with an inverter and the first compressor 143 is driven at a constant speed.
    [00144] Example 11 The garment treatment apparatus, comprising: a drum in which an object is accommodated; at least one evaporator; at least one condenser configured to heat air introduced into the drum; at least one compressor configured to form a heat pump cycle by being combined with at least one condenser and at least one evaporator; and a base frame 160 including a first accommodation portion 161 for accommodating the at least one evaporator and the at least one condenser, a second accommodation portion arranged parallel to the first accommodation portion 162 and for accommodating at least one compressor and one wall 163 formed for dividing the first and second accommodation portions 161 and 162 from each other such that a flow path is formed in the first accommodation portion 161.
    [00145] Example 12 The garment care apparatus according to example 11, wherein a first mounting portion 161c for mounting the first evaporator and a second mounting portion 161d for mounting the first condenser are formed on the first mounting portion 161d. accommodation 161.
    [00146] Example 13 The garment care apparatus according to example 12, wherein the first and second mounting portions 161c and 161d are spaced apart along the wall 163 such that a space is formed between the first evaporator and the first condenser.
    [00147] Example 14 The garment treatment apparatus according to example 13, wherein air introduced into the drum is heated by the first and second heat pump cycles, wherein the first evaporator and the first condenser are provided in the first heat pump cycle, and wherein a second evaporator and a second condenser provided in the second heat pump cycle are arranged between the first and second mounting portions.
    [00148] Example 15 The garment care apparatus according to example 11, wherein an inlet 161a and an outlet 161b of the flow path are formed on either side of the first accommodation portion, and wherein the at least one evaporator and the at least one capacitor are arranged on two sides of the first accommodation portion.
    [00149] Example 16. The garment care apparatus according to example 11, wherein a plurality of compressor mounting portions 162a and 162b are arranged in the second accommodation portion 162 along the flow path of the first portion accommodation 161.
    [00150] Example 17 The garment treatment apparatus according to example 16, wherein air introduced into the drum is heated by the first and second heat pump cycles, and wherein the first compressor of the first heat pump cycle is disposed at one 162a among the plurality of compressor mounting portions, and the second compressor of the second heat pump cycle is disposed at another 162b among the plurality of compressor mounting portions.
    [00151] Example 18 The garment treatment apparatus according to example 17, wherein at least one of the first and second compressors is provided with an inverter to change the drive speed of the compressor through a frequency conversion .
    [00152] Example 19 The garment treatment apparatus according to example 17, wherein the first heat pump cycle is provided with a first evaporator and a first condenser, and the second heat pump cycle is provided with a second evaporator and a second condenser, and wherein the first and second heat pump cycles are arranged such that air introduced into the first accommodation portion 161 passes through the first evaporator, the second evaporator, the second condenser and the first condenser, sequentially.
    [00153] Example 20 The garment care apparatus according to example 16, wherein a compressor is disposed on one of the plurality of compressor mounting portions 162a and 162b and no compressor is disposed on another of the compressor mounting portions 162a and 162b compressor assembly 162a and 162b such that air introduced into the drum is heated by a single heat pump cycle.
    [00154] Example 21 The laundry treatment apparatus according to example 11, wherein a motor 131 of a fan 130 for sucking in air passing through the flow path is mounted on the base frame 160.
    [00155] Example 22 The garment care apparatus according to example 21, wherein the motor 131 is arranged close to the second accommodation portion 162, in a direction parallel to the first accommodation portion 161.
    权利要求:
    Claims (8)
    [0001]
    1. Clothing treatment apparatus, characterized in that it comprises: an accommodation chamber (110), in which an object is accommodated; a first heat pump cycle (140) having a first evaporator (141), a first compressor (143), a first condenser (142) and a first expansion valve (144); a second heat pump cycle (150) having a second evaporator (151), a second compressor (153), a second condenser (152) and a second expansion valve (154), and arranged such that air is introduced into the chamber (110) passes through the first evaporator (141), the second evaporator (151), the second condenser (152) and the first condenser (142), sequentially; and a controller configured to control an operation of the first and second cycles of the heat pump (140, 150), wherein at least one of the first and second compressors (143, 153) is provided with an inverter for changing the speed of driving the compressor through a frequency conversion, and wherein the controller drives at least one of the first compressor (143) and the second compressor (153) within a predefined drive range by controlling the drive speed of at least one of the first and second compressors (143, 153) using the inverter, wherein at least one of the first compressor (143) and the second compressor (153) is driven in a first mode where the drive speed is constant as a first speed and a second mode wherein the drive speed is varied from the first speed to a second speed, and wherein at least one of the first and second compressors (143, 153) is driven at the first speed. first and second modes, and then it is driven into a third mode where the drive speed is maintained as the second speed.
    [0002]
    2. Garment treatment apparatus, according to claim 1, characterized in that when at least one of a peripheral temperature, an amount of the object and an amount of initial moisture content (BMI) of the object is outside a specific range, the controller controls at least one of the first compressor (143) and the second compressor (153) to be driven in the second mode.
    [0003]
    3. Clothing treatment apparatus, according to claim 2, characterized in that an inverter drive frequency is controlled to be reduced at a specific time when at least one of the peripheral temperature, the amount of the object and the amount of initial moisture content (BMI) of the object is greater than an upper threshold value or lower than a lower threshold value within the specified range.
    [0004]
    4. Clothing treatment apparatus, according to claim 2 or 3, characterized in that in a case where at least one of the peripheral temperature, the amount of the object and the amount of initial moisture content (BMI) of the object is greater than an upper limit value within the specified range, the first and second compressors (143, 153) have the same drive speed in the first mode, and one of the first and second compressors (143, 153) that the inverter has its drive speed reduced in the second mode.
    [0005]
    5. Garment treatment apparatus, according to any one of claims 1 to 4, characterized in that the controller controls the drive speed of at least one of the first and second compressors (143, 153), based on at a condensing temperature of the condenser (142, 152) or a discharge temperature of the compressor (143, 153), the temperature detected in at least one of the first and second heat pump cycles (140, 150).
    [0006]
    6. Clothing treatment apparatus, according to claim 5, characterized in that if the condensing temperature of the condenser (142, 152) or the discharge temperature of the compressor (143, 153) is outside a predefined range, the controller determines that at least one of a peripheral temperature, the object quantity, and the object's initial moisture content (BMI) amount is outside a specific range.
    [0007]
    7. Garment treatment apparatus according to any one of claims 1 to 6, characterized in that the predefined trigger range indicates a compression ratio range, and the second compressor (153) is formed to have a ratio compression than the first compressor (143).
    [0008]
    8. Clothing treatment apparatus, according to claim 7, characterized in that the second compressor (153) is provided with an inverter and the first compressor (143) is driven at a constant speed.
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    法律状态:
    2016-09-20| B03A| Publication of a patent application or of a certificate of addition of invention [chapter 3.1 patent gazette]|
    2019-11-19| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2021-11-03| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2022-01-11| 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 28/12/2015, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    KR10-2014-0192542|2014-12-29|
    KR1020140192542A|KR101613966B1|2014-12-29|2014-12-29|Clothes treating apparatus|
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