WO2022068971A1 - 烘干系统及包括该系统的衣物处理设备 - Google Patents

烘干系统及包括该系统的衣物处理设备 Download PDF

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Publication number
WO2022068971A1
WO2022068971A1 PCT/CN2021/131665 CN2021131665W WO2022068971A1 WO 2022068971 A1 WO2022068971 A1 WO 2022068971A1 CN 2021131665 W CN2021131665 W CN 2021131665W WO 2022068971 A1 WO2022068971 A1 WO 2022068971A1
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Prior art keywords
liquid
outlet
inlet
air
heat exchanger
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PCT/CN2021/131665
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English (en)
French (fr)
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WO2022068971A8 (zh
Inventor
罗荣邦
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青岛海尔空调器有限总公司
青岛海尔空调电子有限公司
海尔智家股份有限公司
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Publication of WO2022068971A1 publication Critical patent/WO2022068971A1/zh
Publication of WO2022068971A8 publication Critical patent/WO2022068971A8/zh

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    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F25/00—Washing machines with receptacles, e.g. perforated, having a rotary movement, e.g. oscillatory movement, the receptacle serving both for washing and for centrifugally separating water from the laundry and having further drying means, e.g. using hot air 
    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00—Domestic laundry dryers
    • D06F58/20—General details of domestic laundry dryers 
    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00—Domestic laundry dryers
    • D06F58/20—General details of domestic laundry dryers 
    • D06F58/24—Condensing arrangements

Definitions

  • the present invention relates to the technical field of laundry treatment, in particular to a drying system and a laundry treatment device including the system.
  • FIG. 1 A schematic diagram of an existing heat pump drying system is shown in Figure 1, which mainly includes refrigerant circulation and humid air circulation.
  • the refrigerant cycle mainly includes a compressor 41 , a condenser 42 , a throttling device 43 and an evaporator 44
  • the humid air cycle includes an air duct 51 , a fan 52 and a drying chamber connected to both ends of the air duct 51 .
  • the condenser 42 and the evaporator 44 in the refrigerant circulation are arranged in the air duct 51.
  • the moist air in the drying chamber is driven by the fan 52 to enter the air duct 51 from one end of the air duct 51, and flows through the air duct 51 in turn.
  • the evaporator 44 and the condenser 42 are then returned to the drying chamber through the other end of the air duct 51 .
  • the humid air passes through the evaporator 44, heat exchange occurs with the evaporator 44, the moisture in the humid air is condensed into water droplets and the moisture content decreases. The heat is exchanged and the temperature rises to dry the laundry in the drying chamber.
  • the relative humidity in the drying chamber also decreases, and the temperature of the air heated by the condenser 42 decreases in the drying chamber and enters the evaporator 44.
  • the dehumidification capability of the evaporator 44 is gradually weakened, and the dehumidification effect is getting worse and worse, which causes the drying time of clothes to increase and the power consumption of the system to increase continuously.
  • the present invention provides a drying system, the drying system includes: A refrigerant circulation circuit, which includes a compressor, a condenser, a throttling element and an evaporator connected by a refrigerant pipe; an air circulation circuit, which includes a drying chamber connected by an air pipe, a gas-liquid exchange a heater, the evaporator and the condenser, the drying chamber has a wet air outlet and a dry air inlet, the gas-liquid heat exchanger has an air inlet, an air outlet, a liquid inlet and a liquid outlet, The air inlet is communicated with the moist air outlet, the air outlet is communicated with the inlet of the evaporator, the outlet of the evaporator is communicated with the inlet of the condenser, and the outlet of the condenser is communicated with the inlet of the e
  • the dry air inlet is in communication;
  • the cooling circulation circuit includes a water receiving tray, a water pump and the gas-liquid heat exchanger communicated through a liquid pipe, and the water receiving tray is arranged below the evaporator and is used for
  • the condensed water is collected, the liquid inlet and the liquid outlet are respectively communicated with the water receiving tray, and the water pump is arranged between the liquid inlet/the liquid outlet and the water receiving tray.
  • the gas-liquid heat exchanger is a shell-and-tube heat exchanger
  • the shell-and-tube heat exchanger includes a shell and a heat exchange tube arranged in the shell, so The air inlet and the air outlet are arranged on the casing and communicate with the inside of the casing respectively, and the liquid inlet and the liquid outlet are arranged on the casing and are respectively connected with the exchange. Both ends of the heat pipe are communicated.
  • the shell-and-tube heat exchanger further includes a baffle plate, and the baffle plate is sleeved on the heat exchange tube, so that a folded plate is formed inside the shell. flow channel.
  • the heat exchange tube is a U-shaped tube
  • the shell-and-tube heat exchanger further includes a baffle, and the baffle is fixed to the
  • the inside of the casing is divided into a flow channel with a U-shaped cross section, and the U-shaped pipe is correspondingly arranged in the flow channel.
  • the air inlet and the air outlet are opened on the peripheral side of the casing and correspond to one end of the U-shaped flow channel respectively; and/or the liquid inlet Both the port and the liquid outlet are arranged on the end face of the casing close to the free end of the U-shaped pipe.
  • the air inlet is opened on the casing close to the upstream end of the U-shaped flow channel, and the air outlet is opened near the upper end of the U-shaped flow channel.
  • the liquid inlet is opened on the casing close to the downstream end of the U-shaped pipe, and the liquid outlet is opened on the casing close to the upstream end of the U-shaped pipe.
  • the area of the air inlet is larger than the area of the liquid inlet and the liquid outlet
  • the area of the air outlet is larger than the area of the liquid inlet and the liquid outlet area of the mouth.
  • the drying system further comprises a cascade heat exchanger, the cascade heat exchanger has a first inlet, a first outlet, a second inlet and a second outlet, the The air flow channel formed between the first inlet and the first outlet and the air flow channel formed between the second inlet and the second outlet can cross heat exchange, wherein the first inlet and the moist air The outlet is in communication, the first outlet is in communication with the air inlet, the second inlet is in communication with the outlet of the evaporator, and the second outlet is in communication with the inlet of the condenser.
  • the water pump is arranged between the liquid inlet and the water receiving tray, and the liquid inlet and the outlet of the water pump are connected by a liquid pipe, and the The inlet of the water pump and the water receiving pan are connected by a liquid pipe whose one end is a free end, the water receiving pan is provided with a liquid return port, and the liquid outlet is communicated with the liquid return port through a liquid pipe, The free end extends into the water receiving tray and the free end and the liquid return port are arranged along the diagonal of the water receiving tray.
  • the present application also provides a clothes treatment device, the clothes treatment device comprising the drying system according to any one of the above preferred technical solutions.
  • the drying system includes: a refrigerant circulation loop, and the refrigerant circulation loop includes a compressor, a condenser, a throttling element and an evaporator connected by a refrigerant pipe;
  • Circulation loop the air circulation loop includes a drying chamber, a gas-liquid heat exchanger, an evaporator and a condenser connected by an air duct, the drying chamber has a wet air outlet and a dry air inlet, and the gas-liquid heat exchanger has an air inlet, Air outlet, liquid inlet and liquid outlet, the air inlet is communicated with the wet air outlet, the air outlet is communicated with the inlet of the evaporator, the outlet of the evaporator is communicated with the inlet of the condenser, and the outlet of the condenser is communicated with the dry air inlet;
  • the cooling circulation loop includes a water receiving tray, a water pump and a gas-liquid
  • the present application can reduce the burden on the evaporator, ensure the dehumidification capacity of the evaporator, shorten the drying time, and reduce the drying energy consumption.
  • the air inlet and air outlet of the gas-liquid heat exchanger are respectively connected with the wet air outlet and the inlet of the evaporator, and the liquid inlet and the liquid outlet are respectively connected with the water receiving tray.
  • the compressor, the fan and the water pump start running, the compressor drives the refrigerant to circulate along the refrigerant circulation loop, the water pump drives the condensed water in the water tray to circulate along the cooling circulation loop, and the fan drives the air flow to circulate in the air circulation loop.
  • the humid air in the drying chamber is sucked into the humid air outlet, and the humid air first enters the gas-liquid heat exchanger through the air inlet, and exchanges heat with the condensed water in the cooling circulation circuit in the gas-liquid heat exchanger to reduce the temperature, thereby realizing the preliminary Cooling, the temperature of the corresponding condensed water is increased, the recycling of the cold energy in the condensed water is realized, and the waste of energy is reduced.
  • the wet air whose temperature has been initially lowered is discharged from the gas-liquid heat exchanger from the air outlet and continues to flow forward to the evaporator, where it exchanges heat with the refrigerant to achieve secondary cooling, and the temperature of the air drops below the dew point temperature.
  • the humid air is not directly sent to the evaporator for heat exchange, but first passes through the gas-liquid heat exchanger for heat exchange with the low-temperature condensed water inside, so the humid air reaching the evaporator will be more
  • the temperature of the humid air of the evaporator is lower, that is, the sensible heat load of the evaporator is reduced, and the dehumidification efficiency of the drying system is improved.
  • the condensed water absorbs the heat of the humid air, and the system recovers the latent heat of the condensed water, avoiding low temperature.
  • the condensed water is not effectively used, which reduces the loss of energy, improves the circulation efficiency of the system, and reduces the energy consumption.
  • the gas-liquid heat exchanger of the present application has the advantages of high heat transfer coefficient, fast heat exchange speed, small occupied space, long service life and the like.
  • baffle channel is formed inside the shell, which can increase the heat exchange area between the air and the heat exchange tube, thereby greatly improving the heat exchange effect and reducing the efficiency of the evaporator. burden and improve the dehumidification efficiency of the system.
  • the air can be fully contacted with the heat exchange tube, and the heat exchange effect can be further improved.
  • the air inlet and the air outlet on the peripheral side of the casing and corresponding to one end of the U-shaped flow channel respectively, and by arranging the liquid inlet and the liquid outlet on the end face of the casing close to the free end of the U-shaped pipe
  • the air can exchange heat with the heat exchange tubes to the greatest extent, and improve the heat exchange effect.
  • the air inlet is opened on the casing near the upstream end of the U-shaped flow channel
  • the air outlet is opened on the casing near the downstream end of the U-shaped flow channel
  • the liquid inlet is opened near the downstream of the U-shaped pipe.
  • the liquid outlet is opened on the shell near the upstream end of the U-shaped pipe, so that the flow direction of the air is opposite to the flow direction of the condensed water, and the countercurrent heat exchange between the air and the condensed water is realized, and the heat exchange effect is better.
  • the condensed water is a liquid
  • the pressure drop is small
  • the air is a gas
  • the pressure drop is large. Therefore, the area of the air inlet is larger than the area of the liquid inlet and the liquid outlet, and the area of the air outlet is larger than that of the liquid inlet and the liquid outlet.
  • the area of the liquid outlet can reduce the pressure drop of the air and achieve a better flow heat transfer effect.
  • the drying system can also improve the heat exchange efficiency of the evaporator and the condenser, and achieve higher dehumidification efficiency and lower energy consumption.
  • the first inlet of the cascade heat exchanger is communicated with the humid air outlet
  • the first outlet is communicated with the air inlet of the gas-liquid heat exchanger
  • the second inlet is communicated with the outlet of the evaporator
  • the second outlet is communicated with the outlet of the condenser.
  • the inlet is connected, so that before entering the gas-liquid heat exchanger for cooling, the wet air first exchanges heat with the low-temperature dry air flowing out of the evaporator through the cascade heat exchanger, and its temperature is greatly reduced, and the temperature of the low-temperature dry air is greatly reduced.
  • the process is equal heat exchange
  • the humid air whose temperature has been lowered continues to flow forward to the gas-liquid heat exchanger and the evaporator for secondary and tertiary cooling to reach the dew point temperature below the dew point temperature.
  • Moisture is greatly separated, because in this process, the wet air is not directly sent to the evaporator for heat exchange, but firstly exchanges heat with the low-temperature dry air from the evaporator through the cascade heat exchanger, and then passes through the gas-liquid heat exchanger. The secondary heat exchange is carried out, and finally it enters the evaporator for heat exchange.
  • the temperature of the humid air reaching the evaporator will be much lower than that of the humid air directly sent to the evaporator, thus greatly reducing the burden on the evaporator and improving the efficiency of the evaporator.
  • the dehumidification efficiency has been repeatedly tested, observed, analyzed and compared by the inventors. When the cascade heat exchanger and the gas-liquid heat exchanger are used at the same time, the overall dehumidification efficiency can be significantly improved by more than 15%.
  • the temperature of the air entering the condenser is also higher than the temperature of the air entering the condenser without a cascade heat exchanger.
  • the temperature of the air that is discharged and re-entered into the drying chamber is also higher than that without the cascade heat exchanger. Therefore, the setting of the cascade heat exchanger also increases the temperature of the air entering the drying chamber, and accordingly speeds up the drying of the clothes. The drying speed further improves the drying efficiency and further reduces the energy consumption.
  • drying efficiency can be significantly improved and drying energy consumption can be reduced.
  • FIG. 1 is a system schematic diagram of a heat pump drying system in the prior art
  • Fig. 2 is the system diagram of the drying system in the first embodiment of the present invention.
  • Fig. 3 is the system diagram of the drying system in the second embodiment of the present invention.
  • FIG. 4 is a structural diagram of a specific embodiment of the gas-liquid heat exchanger of the present invention.
  • the terms “installed”, “connected” and “connected” should be understood in a broad sense, for example, it may be a fixed connection or a It is a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected, or indirectly connected through an intermediate medium, or it can be the internal communication between two components.
  • installed should be understood in a broad sense, for example, it may be a fixed connection or a It is a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected, or indirectly connected through an intermediate medium, or it can be the internal communication between two components.
  • FIG. 2 is a system diagram of the drying system in the first embodiment of the present invention.
  • the relative humidity in the drying chamber also decreases, and the air heated by the condenser is placed in the drying chamber.
  • the reduction of the medium temperature also decreases, and the temperature of the air entering the evaporator and the condenser continues to rise, resulting in a gradual weakening of the dehumidification capacity of the evaporator, and the dehumidification effect is getting worse and worse. also growing.
  • the drying system of the present application includes a refrigerant circulation circuit, an air circulation circuit and a cooling circulation circuit.
  • the refrigerant circulation circuit includes a compressor 11 , a condenser 12 , a throttle element 13 and an evaporator 14 , and the above components are connected in sequence through a refrigerant pipe 15 .
  • the air circulation loop includes a drying chamber 21, a gas-liquid heat exchanger 23, an evaporator 14 and a condenser 12 connected by an air duct 25.
  • the drying chamber 21 has a wet air outlet 211 and a dry air inlet 212
  • the gas-liquid heat exchanger 23 has an air inlet 2311, an air outlet 2312, a liquid inlet 2313 and a liquid outlet 2314
  • the air inlet 2311 is communicated with the wet air outlet 211
  • the air outlet 2312 is communicated with the inlet of the evaporator 14
  • the outlet of the evaporator 14 is communicated with the condenser
  • the inlet of the condenser 12 is communicated with
  • the outlet of the condenser 12 is communicated with the dry air inlet 212
  • a fan 24 is arranged in the air circulation circuit.
  • the cooling circulation loop includes a water receiving pan 31, a water pump 32 and a gas-liquid heat exchanger 23 communicated through a liquid pipe 33.
  • the water receiving pan 31 is arranged below the evaporator 14 and is used to collect the condensed water separated from the air, and the gas-liquid exchange
  • the liquid inlet 2313 and the liquid outlet 2314 of the heater 23 are respectively communicated with the water receiving tray 31 .
  • the compressor 11, the fan 24 and the water pump 32 start to run.
  • the refrigerant discharged from the exhaust port of the compressor 11 passes through the condenser 12, the throttling element 13 and the evaporator 14 in sequence, and then returns to the compressor 11 from the suction port of the compressor 11 to complete the refrigerant cycle (the refrigerant circulation path in Fig. solid arrows).
  • the water pump 32 drives the condensed water in the water receiving tray 31 to pass through the gas-liquid heat exchanger 23 and then return to the water receiving tray 31 to complete the cooling cycle.
  • the fan 24 drives the air flow in the drying chamber 21 to pass through the gas-liquid heat exchanger 23, the evaporator 14, and the condenser 12 in turn, and then returns to the drying chamber 21 to complete the air circulation (the air circulation path is shown by the hollow arrow in FIG. 2). out).
  • the air circulation path is shown by the hollow arrow in FIG. 2). out.
  • the humid air in the drying chamber 21 is sucked into the humid air outlet 211, and the humid air first enters the gas-liquid heat exchanger 23 through the air inlet 2311, and the humid air in the gas-liquid heat exchanger 23 is connected with the air in the cooling cycle.
  • the temperature of the condensed water is reduced by heat exchange, and preliminary cooling is achieved, and the temperature of the corresponding condensed water is increased; the humid air whose temperature is initially reduced is discharged from the gas-liquid heat exchanger 23 through the air outlet 2312 and continues to flow forward to the evaporator. 14.
  • the evaporator 14 performs heat exchange with the low-temperature refrigerant in the refrigerant cycle to achieve secondary cooling.
  • the temperature of the air drops below the dew point temperature to precipitate moisture, which becomes condensed water and drips into the water receiving tray 31 .
  • the air after the secondary cooling becomes dry air and is discharged from the evaporator 14 to the condenser 12.
  • the high temperature refrigerant in the refrigerant cycle is heated by heat exchange, and the heated high temperature air enters through the dry air inlet 212.
  • the laundry is dried in the drying chamber 21 .
  • the air inlet 2311 and the air outlet 2312 of the gas-liquid heat exchanger 23 are respectively communicated with the humid air outlet 211 and the inlet of the evaporator 14, and the liquid inlet 2313 and the liquid outlet 2314 are respectively communicated with the water receiving tray 31,
  • the moist air in the drying chamber 21 is sucked into the moist air outlet 211, and the moist air first enters the gas-liquid heat exchanger 23 through the air inlet 2311, and is connected with the cooling circulation loop in the gas-liquid heat exchanger 23.
  • the temperature of the condensed water in the condensed water is reduced by heat exchange, and preliminary cooling is realized, and the temperature of the corresponding condensed water is raised, so as to realize the recovery and utilization of the cold energy in the condensed water, and reduce the waste of energy.
  • the humid air whose temperature has been initially lowered is discharged from the gas-liquid heat exchanger 23 through the air outlet 2312 and continues to flow forward to the evaporator 14, where it exchanges heat with the refrigerant to achieve secondary cooling, and the temperature of the air is reduced to Below the dew point temperature, moisture is precipitated, and drops into the drain pan 31 as condensed water.
  • the humid air is not directly sent to the evaporator 14 for heat exchange, but firstly passes through the gas-liquid heat exchanger 23 for heat exchange with the low-temperature condensed water inside, so the humid air reaching the evaporator 14 will be more
  • the temperature of the humid air directly sent to the evaporator 14 is lower, that is, the sensible heat burden of the evaporator 14 is reduced, and the dehumidification efficiency of the drying system is improved.
  • the latent heat prevents the low-temperature condensed water from not being effectively used, reduces the loss of energy, improves the circulation efficiency of the system, and reduces the energy consumption.
  • FIG. 4 is a structural diagram of a specific embodiment of the gas-liquid heat exchanger 23 of the present invention.
  • the drying system is applied to an integrated washer-drying machine, which includes a box body (not shown in the figure), and an organic door is arranged on the box body, and the box A washing tub assembly is arranged in the body, the washing tub assembly includes an outer tub and an inner tub, the inner tub can accommodate the clothes to be washed, and the outer tub is provided with the above-mentioned wet air outlet 211 and dry air inlet 212 .
  • the evaporator 14 , the condenser 12 and the fan 24 are each provided with a casing, and an inlet and an outlet connected to the air duct 25 are respectively formed on the casing.
  • the humid air outlet 211 communicates with the air inlet 2311 of the gas-liquid heat exchanger 23 through the air duct 25, and the air outlet 2312 of the air-liquid heat exchanger 23 communicates with the inlet of the evaporator 14 through the air duct 25, and the evaporation
  • the outlet of the condenser 14 is connected to the inlet of the condenser 12 through the air duct 25, the outlet of the condenser 12 is communicated with the inlet of the fan 24 through the air duct 25, and the outlet of the fan 24 is communicated with the dry air inlet 212 through the air duct 25, so as to realize air The connection of the circulation loop.
  • the discharge port of the compressor 11 is communicated with the refrigerant inlet of the condenser 12 through the refrigerant pipe 15, and the refrigerant outlet of the condenser 12 is communicated with one end of the throttling element 13 through the refrigerant pipe 15, and the other end of the throttling element 13 is connected.
  • One end is communicated with the refrigerant inlet of the evaporator 14 through the refrigerant pipe 15, the refrigerant outlet of the evaporator 14 is communicated with the inlet of the gas-liquid separator through the refrigerant pipe 15, and the outlet of the gas-liquid separator (not marked in the figure) is connected with the compressor 11.
  • the suction port is connected to realize the communication of the refrigerant circulation circuit.
  • the throttling element 13 is preferably an electronic expansion valve. Of course, the throttling element 13 can also be a capillary tube or a thermal expansion valve.
  • the water receiving pan 31 communicates with the suction port of the water pump 32 through the liquid pipe 33 with one end being a free end, and the drain port of the water pump 32 communicates with the liquid inlet 2313 of the gas-liquid heat exchanger 23 through the liquid pipe 33.
  • the liquid outlet 2314 of the liquid heat exchanger 23 is communicated with the liquid return port opened on the side wall of the water receiving pan 31 through the liquid pipe 33, so as to realize the communication of the cooling circulation circuit.
  • the free end of the liquid pipe 33 connected to the suction port of the water pump 32 extends into the water receiving tray 31 , and the free end and the liquid return port are arranged along the diagonal of the water receiving tray 31 .
  • the gas-liquid heat exchanger 23 adopts a shell-and-tube heat exchanger, which includes a substantially cylindrical shell 231 and a plurality of heat exchangers disposed in the shell 231 .
  • Heat pipe 232 .
  • the casing 231 is arranged in the vertical direction, and a partition 234 is arranged inside.
  • the partition 234 is extended and fixed upward from the lower part along the length direction of the casing 231. After fixing, the casing 231 is divided into an inverted U-shaped flow. road.
  • the heat exchange tubes 232 are U-shaped tubes, and each heat exchange tube 232 extends along the inverted U-shaped flow channel.
  • the casing 231 is also provided with a plurality of baffles 233, each baffle 233 is provided with a plurality of through holes for allowing the heat exchange tubes 232 to pass through, and the baffles 233 are sleeved on the heat exchange through the plurality of through holes.
  • the tube 232 is fixedly connected to the inner wall of the housing 231 or the partition plate 234 respectively.
  • a plurality of baffles 233 are arranged at intervals, so that each straight section of the U-shaped flow channel is divided into S-shaped baffle channels.
  • the air inlet 2311 and the air outlet 2312 are respectively opened in the lower part of the peripheral side of the housing 231, and the air inlet 2311 and the air outlet 2312 are arranged in the U-shaped in a direction away from each other.
  • the air inlet 2311 is opened near the upstream end of the U-shaped flow channel
  • the air outlet 2312 is opened near the downstream end of the U-shaped flow channel.
  • the casing 231 is also provided with a liquid separation plate 235.
  • the liquid separation plate 235 and the lower end of the casing 231 are separated into a liquid inlet cavity 237 and a liquid outlet cavity 238 by a cavity separation plate 236, and a liquid inlet 2313 and a liquid outlet.
  • the liquid inlet 2313 is located on the side close to the downstream section of the air flow (ie, the right side shown in FIG. 4 )
  • the liquid outlet 2314 is located on the side near the upstream end of the air flow (ie, the left side shown in FIG. 4 ).
  • the area of the air inlet 2311 is larger than that of the liquid inlet 2313 and the liquid outlet 2314
  • the area of the air outlet 2312 is also larger than that of the liquid inlet 2313 and the liquid outlet 2314 .
  • the liquid separator 235 is also provided with a plurality of through holes corresponding to the liquid inlet chamber 237 and the liquid outlet chamber 238, respectively, and the two ends of each U-shaped heat exchange tube 232 are respectively inserted into the liquid separator 235 corresponding to the liquid inlet chamber 237 and the liquid outlet chamber 237.
  • the through holes of the liquid outlet cavity 238 are connected to realize the fixing of the heat exchange tube 232 and the communication between the liquid inlet 2313 and the liquid outlet 2314 and the two ends of the heat exchange tube 232 .
  • the condensed water enters the liquid inlet cavity 237 through the liquid inlet 2313, and is divided into multiple channels and enters a U-shaped pipe respectively.
  • the other end converges to the liquid outlet chamber 238, and finally flows back to the water receiving tray 31 through the liquid outlet 2314 (the condensed water circulation path is shown by the hollow arrow in FIG. 4).
  • the moist air enters the casing 231 through the air inlet 2311, and flows back and forth along the S-shaped baffle channel under the barrier of the baffle plate 233 and the baffle plate 234.
  • the gas-liquid heat exchanger 23 of the present application has the advantages of high heat transfer coefficient, fast heat exchange speed, small occupied space, and long service life.
  • an S-shaped baffle channel is formed inside the shell 231, so that the air and the heat exchange tube 232 are fully contacted, and the air and the heat exchange tube 232 are significantly increased. Therefore, the heat exchange effect is greatly improved, the burden on the evaporator 14 is reduced, and the dehumidification efficiency of the system is improved.
  • the liquid outlet 2314 is opened on the casing 231 near the upstream end of the U-shaped pipe, so that the flow direction of the air is opposite to that of the condensed water, and the countercurrent heat exchange between the air and the condensed water is realized. The effect is better.
  • the liquid return port and the free end of the liquid pipe 33 along the diagonal of the water receiving tray 31, uneven temperature distribution of the condensed water can also be avoided, and the heat exchange effect of the condensed water can be improved.
  • the condensed water is liquid, the pressure drop is small, and the air is gas, and the pressure drop is large. Therefore, the area of the air inlet 2311 is larger than that of the liquid inlet 2313 and the liquid outlet 2314, and the area of the air outlet 2312 is larger than that of the liquid inlet.
  • the area of 2313 and the liquid outlet 2314 can reduce the pressure drop of the air and achieve better flow heat exchange effect.
  • 3 is a system diagram of the drying system in the second embodiment of the present invention.
  • the drying system further includes a cascade heat exchanger 22, and the cascade heat exchanger 22 has a first inlet 221, a first outlet 222, The second inlet 223 and the second outlet 224, an air flow channel is formed between the first inlet 221 and the first outlet 222, another air flow channel is formed between the second inlet 223 and the second outlet 224, two air flow channels They are arranged to cross each other, so that heat can be cross-exchanged.
  • the first inlet 221 is communicated with the humid air outlet 211
  • the first outlet 222 is communicated with the air inlet 2311 of the gas-liquid heat exchanger 23
  • the second inlet 223 is communicated with the outlet of the evaporator 14, and the second outlet 224 is communicated with the outlet of the condenser 12.
  • Inlet connection does not limit the specific structural form of the cascade heat exchanger 22 , and any heat exchanger that can satisfy the above conditions can be used as the cascade heat exchanger 22 in the present application.
  • a plate-fin heat exchanger or a rotary heat exchanger can be used as the cascade heat exchanger 22 of the present application, or the like.
  • the high-temperature humid air discharged from the humid air outlet 211 first flows into the cascade heat exchanger 22 through the first inlet 221 of the cascade heat exchanger 22 .
  • the humid air whose temperature has been lowered continues to flow forward to the gas-liquid heat exchanger 23 for secondary temperature reduction, and at the same time, the dry air whose temperature has been raised continues to flow forward to the condenser 12 for secondary heating.
  • the drying system can simultaneously improve the heat exchange efficiency of the evaporator 14 and the condenser 12, thereby achieving higher dehumidification efficiency and lower energy consumption.
  • the humid air before entering the gas-liquid heat exchanger 23 for cooling, the humid air first exchanges heat with the low-temperature dry air flowing out of the evaporator 14 through the cascade heat exchanger 22, and its temperature is greatly reduced, and the temperature of the low-temperature dry air is simultaneously After being raised (this process is equal heat exchange), the humid air whose temperature has been lowered continues to flow forward to the gas-liquid heat exchanger 23 and the evaporator 14 for secondary and tertiary cooling to reach below the dew point temperature.
  • the moisture is greatly precipitated, because in this process, the wet air is not directly sent to the evaporator 14 for heat exchange, but firstly passes through the cascade heat exchanger 22 to exchange heat with the low-temperature dry air from the evaporator 14, and then passes through the air.
  • the liquid heat exchanger 23 performs secondary heat exchange, and finally enters the evaporator 14 for heat exchange. Therefore, the temperature of the humid air reaching the evaporator 14 will be much lower than that of the humid air directly sent to the evaporator 14, thus greatly reducing the temperature.
  • the burden of the evaporator 14 is reduced, and the dehumidification efficiency is improved. After repeated tests, observations, analysis and comparisons by the inventor, when the cascade heat exchanger 22 and the gas-liquid heat exchanger 23 are used at the same time, the overall dehumidification efficiency of more than 15% can be achieved. Significantly increased.
  • the temperature of the air entering the condenser 12 is also higher than the temperature of the air entering the condenser 12 directly without the cascade heat exchanger 22.
  • the temperature of the air discharged through the condenser 12 and re-entering the drying chamber 21 is also higher than that when the cascade heat exchanger 22 is not provided. Therefore, the setting of the cascade heat exchanger 22 also improves the air entering the drying chamber 21. The temperature increases the drying speed of the clothes accordingly, which further improves the drying efficiency and further reduces the energy consumption.
  • the specific arrangement of the shell-and-tube heat exchanger is not limited to the above-mentioned manner, and those skilled in the art can adjust it as long as the arrangement can realize the connection between the condensed water and the air. heat exchange can be done.
  • the setting positions of the air inlet 2311, the air outlet 2312, the liquid inlet 2313 and the liquid outlet 2314 can be adjusted based on the actual product. They can be arranged away from each other or collinearly arranged along the length direction of the shell 231; the specific form and quantity of the heat exchange tubes 232 can be adjusted, such as straight tubes or S-shaped tubes, etc.; One or all of them can be optionally omitted, etc.
  • the arrangement of the evaporator 14, the condenser 12 and the fan 24 is not static.
  • the air circulation loop can be formed, those skilled in the art can adjust the arrangement of the above components.
  • the arrangement is changed without departing from the principles of the present application.
  • one or more of the evaporator 14 , the condenser 12 and the fan 24 may also be directly disposed inside the air duct 25 .
  • the embodiment of the gas-liquid heat exchanger 23 is not limited to this, and those skilled in the art can The selection is based on the actual application scenario, and the effect is not significant compared to the shell and tube heat exchanger.
  • the gas-liquid heat exchanger 23 can also be a plate heat exchanger or a casing heat exchanger, etc. When a casing heat exchanger is used, it can be set so that the air goes through the outer tube and the condensed water goes through the inner tube, so as to take into account the flow heat exchange Effect.
  • the application also provides an integrated washing and drying machine, the integrated washing and drying machine includes a box body (not shown in the figure), the box body is provided with an organic door, and the box body is provided with a water inlet assembly, a driving device and a washing tub assembly,
  • the washing tub assembly includes an outer tub and an inner tub, the inner tub can accommodate the clothes to be washed, the water inlet assembly can inject water into the outer tub, and the driving device can drive the inner tub to rotate to complete the washing of the clothes.
  • the washer-drying machine also includes the drying system described in the above-mentioned embodiments, the outer cylinder is provided with a wet air outlet 211 and a dry air inlet 212, the outer cylinder, the gas-liquid heat exchanger 23, the evaporator 14, and the condenser 12 It is connected with the fan 24 through the air duct 25 to form an air circulation loop.
  • the drying efficiency of the washer-drying machine can be significantly improved, and the drying energy consumption can be reduced.

Abstract

一种烘干系统及包括该系统的衣物处理设备。烘干系统包括：冷媒循环回路，包括压缩机（11）、冷凝器（12）、节流元件（13）和蒸发器（14）；空气循环回路，包括干燥腔室（21）、气液换热器（23）、蒸发器（14）和冷凝器（12），气液换热器（23）的进气口（2311）与干燥腔室（21）的湿空气出口（211）连通，出气口（2312）与蒸发器（14）的进口连通，蒸发器（14）的出口与冷凝器（12）的进口连通，冷凝器（12）的出口与干燥腔室（21）的干空气进口（212）连通；冷却循环回路，包括接水盘（31）、水泵（32）和气液换热器（23），气液换热器（23）的进液口（2313）和出液口（2314）分别与接水盘（31）连通，水泵（32）设置于出液口（2314）与接水盘（31）之间。保证蒸发器（14）的除湿能力，缩短烘干时间，降低烘干能耗。

Description

烘干系统及包括该系统的衣物处理设备 技术领域
本发明涉及衣物处理技术领域，具体涉及一种烘干系统及包括该系统的衣物处理设备。
背景技术
现有的热泵式烘干系统的示意图如图1所示，其主要包括冷媒循环和湿空气循环。其中，冷媒循环主要包括压缩机41、冷凝器42、节流装置43和蒸发器44，湿空气循环包括风道51、风机52以及分别与风道51两端连通的干燥腔室。冷媒循环中的冷凝器42和蒸发器44设置在风道51中，运行过程中，干燥腔室内的湿空气在风机52的带动下由风道51的一端进入风道51，并在依次流过蒸发器44和冷凝器42后由风道51的另一端返回干燥腔室。当湿空气经过蒸发器44时与蒸发器44发生热交换，湿空气中的水分冷凝为水滴析出而含湿量下降，含湿量下降的湿空气再经过冷凝器42时，与冷凝器42发生热交换而温度上升，以对干燥腔室内的衣物进行烘干。
但是，随着干燥腔室内衣物的含水率逐渐降低，干燥腔室内的相对湿度也越来越小，经过冷凝器42加热后的空气在干燥腔室中温度降低幅度也减小，进入蒸发器44和冷凝器42的空气温度不断升高，导致蒸发器44的除湿能力逐渐减弱，除湿效果越来越差，这样就造成烘干衣物时间加长，系统功耗也不断增大。
相应地，本领域需要一种新的烘干系统及包括该系统的衣物处理设备来解决上述问题。
发明内容
为了解决现有技术中的上述至少一个问题，即为了解决现有烘干系统存在的烘干时间长、能耗大的问题，本发明提供了一种烘干系统，所述烘干系统包括：冷媒循环回路，所述冷媒循环回路包括通过冷媒管连接的压缩机、冷凝器、节流元件和蒸发器；空气循环回路，所述 空气循环回路包括通过风管连接的干燥腔室、气液换热器、所述蒸发器和所述冷凝器，所述干燥腔室具有湿空气出口和干空气进口，所述气液换热器具有进气口、出气口、进液口和出液口，所述进气口与所述湿空气出口连通，所述出气口与所述蒸发器的进口连通，所述蒸发器的出口与所述冷凝器的进口连通，所述冷凝器的出口与所述干空气进口连通；冷却循环回路，所述冷却循环回路包括通过液管连通的接水盘、水泵和所述气液换热器，所述接水盘设置于所述蒸发器的下方，用于收集冷凝水，所述进液口和所述出液口分别与所述接水盘连通，所述水泵设置于所述进液口/所述出液口与所述接水盘之间。
在上述烘干系统的优选技术方案中，所述气液换热器为管壳式换热器，所述管壳式换热器包括壳体和设置于所述壳体内的换热管，所述进气口和所述出气口设置于所述壳体上且分别与所述壳体内部连通，所述进液口和所述出液口设置于所述壳体上且分别与所述换热管的两端连通。
在上述烘干系统的优选技术方案中，所述管壳式换热器还包括折流板，所述折流板套设在所述换热管上，从而使得所述壳体内部形成有折流通道。
在上述烘干系统的优选技术方案中，所述换热管为U型管，所述管壳式换热器还包括隔板，所述隔板沿所述壳体的长度方向固定于所述壳体内并将所述壳体内部分隔为截面为U型的流道，所述U型管对应设置于所述流道内。
在上述烘干系统的优选技术方案中，所述进气口和所述出气口开设于所述壳体的周侧且分别对应所述U型的流道的一端；并且/或者所述进液口和所述出液口均设置于所述壳体靠近所述U型管的自由端的端面上。
在上述烘干系统的优选技术方案中，沿所述空气的流动方向，所述进气口开设于靠近所述U型的流道的上游端的壳体上，所述出气口开设于靠近所述U型的流道的下游端的壳体上，所述进液口开设于靠近所述U型管下游端的壳体上，所述出液口开设于靠近所述U型管上游端的壳体上。
在上述烘干系统的优选技术方案中，所述进气口的面积大于所述进液口和所述出液口的面积，所述出气口的面积大于所述进液口和所述出液口的面积。
在上述烘干系统的优选技术方案中，所述烘干系统还包括复叠换热器，所述复叠换热器具有第一进口、第一出口、第二进口和第二出口，所述第一进口与第一出口之间形成的空气流道与所述第二进口与所述第二出口之间形成的空气流道能够交叉换热，其中，所述第一进口与所述湿空气出口连通，所述第一出口与所述进气口连通，所述第二进口与所述蒸发器的出口连通，所述第二出口与所述冷凝器的进口连通。
在上述烘干系统的优选技术方案中，所述水泵设置于所述进液口与所述接水盘之间，所述进液口与所述水泵的出口之间通过液管连接，所述水泵的进口与所述接水盘之间通过一端为自由端的液管连接，所述接水盘上设置有回液口，所述出液口与所述回液口之间通过液管连通，所述自由端伸入所述接水盘并且所述自由端与所述回液口沿所述接水盘的对角线设置。
本申请还提供了一种衣物处理设备，所述衣物处理设备包括上述优选技术方案中任一项所述的烘干系统。
本领域技术人员能够理解的是，在本发明的优选技术方案中，烘干系统包括：冷媒循环回路，冷媒循环回路包括通过冷媒管连接的压缩机、冷凝器、节流元件和蒸发器；空气循环回路，空气循环回路包括通过风管连接的干燥腔室、气液换热器、蒸发器和冷凝器，干燥腔室具有湿空气出口和干空气进口，气液换热器具有进气口、出气口、进液口和出液口，进气口与湿空气出口连通，出气口与蒸发器的进口连通，蒸发器的出口与冷凝器的进口连通，冷凝器的出口与干空气进口连通；冷却循环回路，冷却循环回路包括通过液管连通的接水盘、水泵和气液换热器，接水盘设置于蒸发器的下方，用于收集冷凝水，进液口和出液口分别与接水盘连通，水泵设置于进液口/出液口与接水盘之间。
通过在烘干系统中设置气液换热器，本申请能够减轻蒸发器的负担，保证蒸发器的除湿能力，缩短烘干时间，降低烘干能耗。
具体而言，气液换热器的进气口和出气口分别与湿空气出口和蒸发器的进口连通，进液口和出液口分别与接水盘连通，在烘干系统 工作时，压缩机、风机和水泵启动运行，压缩机推动冷媒沿冷媒循环回路循环，水泵带动接水盘中的冷凝水沿冷却循环回路循环，风机带动空气流在空气循环回路循环。干燥腔室内的湿空气被吸入湿空气出口，湿空气首先通过进气口进入气液换热器，在气液换热器内与冷却循环回路中的冷凝水进行热交换而温度降低，实现初步冷却，相应的冷凝水的温度被升高，实现冷凝水中冷量的回收利用，减少能源的浪费。温度被初步降低后的湿空气由出气口排出气液换热器并继续向前流动至蒸发器，在蒸发器中与冷媒进行热交换而实现二次降温，空气的温度降低至露点温度以下而析出水分，变为冷凝水滴入接水盘中。由于在此过程中湿空气不是直接被送到蒸发器进行热交换，而是先通过气液换热器的与里面的低温冷凝水进行热交换，因此到达蒸发器的湿空气将比直接送到蒸发器的湿空气的温度更低，也即减轻了蒸发器的显热负担，提高了烘干系统的除湿效率，同时冷凝水吸收湿空气的热量，系统回收了冷凝水的潜热，避免了低温的冷凝水没有被有效利用，减少了能量的损失，使系统循环效率提高，能耗降低。
进一步地，通过采用管壳式换热器，使得本申请的气液换热器具有传热系数高、换热速度快、占用空间小、寿命长等优点。
进一步地，通过在管壳式换热器内设置折流板，使得壳体内部形成折流通道，能够增加空气与换热管的换热面积，从而大幅提高换热效果，进而降低蒸发器的负担，提高系统的除湿效率。
进一步地，通过在壳体内设置隔板将壳体内部分隔为U型的流道，能够使得空气与换热管充分接触，进一步提高换热效果。
进一步地，通过将进气口和出气口设置在壳体的周侧且分别对应U型流道的一端，以及将进液口和出液口均设置于壳体靠近U型管的自由端的端面上，使得空气在进入管壳式换热器后能够与换热管最大程度的进行热交换，提高换热效果。
进一步地，通过将进气口开设于靠近U型的流道的上游端的壳体上，出气口开设于靠近U型的流道的下游端的壳体上，进液口开设于靠近U型管下游端的壳体上，出液口开设于靠近U型管上游端的壳体上，使得空气的流向与冷凝水的流向相反，实现空气与冷凝水之间的逆流换热，换热效果较佳。
进一步地，由于冷凝水为液体，压降较小，空气为气体，压降较大，因此将进气口的面积大于进液口和出液口的面积，出气口的面积大于进液口和出液口的面积，能够减小空气的压降，实现较好的流动换热效果。
进一步地，通过在烘干系统设置复叠换热器，还使得烘干系统能够同时提高蒸发器与冷凝器的换热效率，实现更高的除湿效率和更低的能耗。
具体地，复叠换热器的第一进口与湿空气出口连通，第一出口与气液换热器的进气口连通，第二进口与蒸发器的出口连通，第二出口与冷凝器的进口连通，这样一来，湿空气在进入气液换热器进行冷却前，首先通过复叠换热器与流出蒸发器的低温干空气进行热交换，其温度被大幅降低，低温干空气的温度同时被升高(该过程是等量热交换)，温度被降低后的湿空气继续向前依次流动到气液换热器和蒸发器进行二次和三次降温而达到露点温度以下，空气中的水分大幅析出，由于在此过程中湿空气不是直接送到蒸发器进行热交换，而是先通过复叠换热器与来自蒸发器的低温干空气进行热交换，然后再经过气液换热器进行二次热交换，最后才进入蒸发器进行热交换，因此，到达蒸发器的湿空气将比直接送到蒸发器的湿空气的温度低很多，因而大幅度减轻了蒸发器的负担，提高了除湿效率，经发明人反复试验、观测、分析和比较，在同时采用复叠换热器和气液换热器时，可实现整体除湿效率15％以上的显著提高。
与此同时，由于蒸发器流出的低温干空气与湿空气进行了热交换，因此进入冷凝器的空气温度也比不设置复叠换热器而直接进如冷凝器的温度高，这样经过冷凝器排出再次进入干燥腔室的空气温度也要比不设置复叠换热器时要高，因此，复叠换热器的设置也提高了进入干燥腔室的空气的温度，相应地加快了衣物的烘干速度，使得干燥效率进一步提升，能耗进一步下降。
本申请的衣物处理设备，通过设置上述的烘干系统，能够显著提升烘干效率，降低烘干能耗。
附图说明
下面参照附图并结合洗干一体机来描述本发明的烘干系统及包括该系统的衣物处理设备。附图中：
图1为现有技术中的热泵式烘干系统的系统示意图；
图2为本发明的第一种实施方式中烘干系统的系统图；
图3为本发明的第二种实施方式中烘干系统的系统图；
图4为本发明的气液换热器的一种具体实施方式的结构图。
附图标记列表
11、压缩机；12、冷凝器；13、节流元件；14、蒸发器；15、冷媒管；21、干燥腔室；211、湿空气出口；212、干空气进口；22、复叠换热器；221、第一进口；222、第一出口；223、第二进口；224、第二出口；23、气液换热器；231、壳体；2311、进气口；2312、出气口；2313、进液口；2314、出液口；232、换热管；233、折流板；234、隔板；235、分液板；236、分腔板；237、进液腔；238、出液腔；24、风机；25、风管；31、接水盘；32、水泵；33、液管；41、压缩机；42、冷凝器；43、节流装置；44、蒸发器；51、风道；52、风机。
具体实施方式
下面参照附图来描述本发明的优选实施方式。本领域技术人员应当理解的是，这些实施方式仅仅用于解释本发明的技术原理，并非旨在限制本发明的保护范围。例如，虽然本实施方式是结合洗干一体机进行介绍的，但是这并非旨在于限制本发明的保护范围，在不偏离本发明原理的条件下，本领域技术人员可以将本发明应用于其他衣物处理设备。例如，本申请的烘干系统还能够应用于干衣机、烘鞋机等。
需要说明的是，在本发明的描述中，术语“中心”、“上”、“下”、“左”、“右”、“竖直”、“水平”、“内”、“外”等指示的方向或位置关系的术语是基于附图所示的方向或位置关系，这仅仅是为了便于描述，而不是指示或暗示所述装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。此外，术语“第一”、“第二”、“第三”仅用于描述目的，而不能理解为指示或暗示相对重要性。
此外，还需要说明的是，在本发明的描述中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”应做广义理解，例如，可以 是固定连接，也可以是可拆卸连接，或一体地连接；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通。对于本领域技术人员而言，可根据具体情况理解上述术语在本发明中的具体含义。
实施例1
首先参照图2，对本发明的烘干系统的第一种实施方式进行描述。其中，图2为本发明的第一种实施方式中烘干系统的系统图。
如背景技术中所述，现有的烘干系统中，随着干燥腔室内衣物的含水率逐渐降低，干燥腔室内的相对湿度也越来越小，经过冷凝器加热后的空气在干燥腔室中温度降低幅度也减小，进入蒸发器和冷凝器的空气温度不断升高，导致蒸发器的除湿能力逐渐减弱，除湿效果越来越差，这样就造成干烘干衣物时间加长，系统功耗也不断增大。
如图2所示，为了解决上述问题，本申请的烘干系统包括冷媒循环回路、空气循环回路和冷却循环回路。冷媒循环回路包括压缩机11、冷凝器12、节流元件13和蒸发器14，上述部件通过冷媒管15依次顺序连接。空气循环回路包括通过风管25连接的干燥腔室21、气液换热器23、蒸发器14和冷凝器12，干燥腔室21具有湿空气出口211和干空气进口212，气液换热器23具有进气口2311、出气口2312、进液口2313和出液口2314，进气口2311与湿空气出口211连通，出气口2312与蒸发器14的进口连通，蒸发器14的出口与冷凝器12的进口连通，冷凝器12的出口与干空气进口212连通，空气循环回路中设置有风机24。冷却循环回路包括通过液管33连通的接水盘31、水泵32和气液换热器23，接水盘31设置在蒸发器14的下方，其用于收集空气中析出的冷凝水，气液换热器23的进液口2313和出液口2314分别与接水盘31连通，水泵32设置于进液口2313/出液口2314与接水盘31之间。
烘干系统工作时，压缩机11、风机24和水泵32启动运行。压缩机11排气口排出的冷媒在依次经过冷凝器12、节流元件13和蒸发器14后从压缩机11的吸气口回到压缩机11，完成冷媒循环(冷媒循环路径图2中以实心箭头示出)。水泵32带动接水盘31中的冷凝水经过气液换热器23后回到接水盘31中，完成冷却循环。风机24带动干燥腔室21内的空气流依次经过气液换热器23、蒸发器14、冷凝器12后回到 干燥腔室21内，完成空气循环(空气循环路径图2中以空心箭头示出)。其中，空气循环中，干燥腔室21内的湿空气被吸入湿空气出口211，湿空气首先通过进气口2311进入气液换热器23，在气液换热器23内与冷却循环中的冷凝水进行热交换而温度降低，实现初步冷却，相应的冷凝水的温度被升高；温度被初步降低后的湿空气由出气口2312排出气液换热器23并继续向前流动至蒸发器14，在蒸发器14中与冷媒循环中的低温冷媒进行热交换而实现二次降温，空气的温度降低至露点温度以下而析出水分，水分变为冷凝水滴入接水盘31中。二次降温后的空气变为干空气由蒸发器14排出至冷凝器12，在冷凝器12中于冷媒循环中的高温冷媒进行热交换而实现升温，升温后的高温空气通过干空气进口212进入干燥腔室21内对衣物进行烘干。
通过上述描述可知，本申请通过在烘干系统中设置气液换热器23，能够减轻蒸发器14的负担，保证蒸发器14的除湿能力，缩短烘干时间，降低烘干能耗。
具体而言，气液换热器23的进气口2311和出气口2312分别与湿空气出口211和蒸发器14的进口连通，进液口2313和出液口2314分别与接水盘31连通，在烘干系统工作时，干燥腔室21内的湿空气被吸入湿空气出口211，湿空气首先通过进气口2311进入气液换热器23，在气液换热器23内与冷却循环回路中的冷凝水进行热交换而温度降低，实现初步冷却，相应的冷凝水的温度被升高，实现冷凝水中冷量的回收利用，减少能源的浪费。温度被初步降低后的湿空气由出气口2312排出气液换热器23并继续向前流动至蒸发器14，在蒸发器14中与冷媒进行热交换而实现二次降温，空气的温度降低至露点温度以下而析出水分，变为冷凝水滴入接水盘31中。由于在此过程中湿空气不是直接被送到蒸发器14进行热交换，而是先通过气液换热器23的与里面的低温冷凝水进行热交换，因此到达蒸发器14的湿空气将比直接送到蒸发器14的湿空气的温度更低，也即减轻了蒸发器14的显热负担，提高了烘干系统的除湿效率，同时冷凝水吸收湿空气的热量，系统回收了冷凝水的潜热，避免了低温的冷凝水没有被有效利用，减少了能量的损失，使系统循环效率提高，能耗降低。
下面进一步参照图2和图4，对本申请的烘干系统的第一种实施方式进行详细描述。其中，图4为本发明的气液换热器23的一种具体实施方式的结构图。
如图2所示，在一种可能的实施方式中，烘干系统应用于洗干一体机中，该洗干一体机包括箱体(图中未标出)，箱体上设置有机门，箱体内设置有洗涤筒组件，洗涤筒组件包括外筒和内筒，内筒能够容纳待洗涤衣物，外筒上开设有上述的湿空气出口211和干空气进口212。蒸发器14、冷凝器12和风机24各自带有外壳，外壳上分别形成有与风管25连接的进口和出口。按照空气流动方向，湿空气出口211通过风管25与气液换热器23的进气口2311连通，气液换热器23的出气口2312通过风管25与蒸发器14的进口连通，蒸发器14的出口通过风管25与冷凝器12的进口连接，冷凝器12的出口通过风管25与风机24的进口连通，风机24的出口通过风管25与干空气进口212连通，从而实现空气循环回路的连通。
按照冷媒流动方向，压缩机11的排气口通过冷媒管15与冷凝器12的冷媒进口连通，冷凝器12的冷媒出口通过冷媒管15与节流元件13的一端连通，节流元件13的另一端通过冷媒管15与蒸发器14的冷媒进口连通，蒸发器14的冷媒出口通过冷媒管15与气液分离器的进口连通，气液分离器(图中未标出)的出口与压缩机11的吸气口连通，从而实现冷媒循环回路的连通。其中，节流元件13优选的为电子膨胀阀，当然节流元件13还可以为毛细管或热力膨胀阀等。
按照冷凝水流动方向，接水盘31通过一端为自由端的液管33与水泵32的吸水口连通，水泵32的排水口通过液管33与气液换热器23的进液口2313连通，气液换热器23的出液口2314通过液管33与接水盘31的侧壁上开设的回液口连通，从而实现冷却循环回路的连通。其中，与水泵32的吸水口连接的液管33的自由端伸入接水盘31内，且该自由端与回液口沿接水盘31的对角线设置。
参照图4，在一种较为优选的实施方式中，气液换热器23采用管壳式换热器，其包括大致成圆筒状的壳体231和设置于壳体231内的多根换热管232。壳体231沿竖直方向布置，其内部设置有隔板234，隔板234沿壳体231的长度方向由下部向上延伸固定，固定好后，壳体 231被分隔成截面为倒U型的流道。换热管232为U型管，每个换热管232沿倒U型的流道延伸设置。壳体231内还设置有多个折流板233，每个折流板233上开设有多个允许换热管232穿过的通孔，折流板233通过多个通孔套设在换热管232上，并分别与壳体231内壁或隔板234固定连接。多个折流板233间隔设置，从而使得U型流道的每一直线段又被分隔为S型的折流通道。
继续参照图4，按照壳体231的布置方向，进气口2311和出气口2312分别开设在壳体231的周侧下部，且进气口2311和出气口2312以相背离的方向设置于U型的流道的两端，其中进气口2311靠近U型的流道的上游端开设，出气口2312靠近U型的流道的下游端开设。壳体231内还设置有分液板235，分液板235与壳体231的下端部之间通过分腔板236分隔为进液腔237和出液腔238，进液口2313和出液口2314分别设置于壳体231的下端部对应于进液腔237和出液腔238的位置，并且进液口2313位于靠近空气流动的下游段的一侧(即图4中所示的右侧)，出液口2314位于靠近空气流动的上游端的一侧(即图4中所示的左侧)。开设好后，进气口2311的面积大于进液口2313和出液口2314的面积，出气口2312的面积也大于进液口2313和出液口2314的面积。分液板235上对应进液腔237和出液腔238还分别设置有多个通孔，每根U型换热管232的两端分别插设于分液板235对应于进液腔237和出液腔238的通孔上，从而实现换热管232的固定，以及进液口2313和出液口2314与换热管232两端的连通。
按照图4方位，在水泵32的带动下，冷凝水通过进液口2313进入进液腔237内并分流为多路分别进入一根U型管，在流经U型管后通过U型管的另一端汇流至出液腔238，最终通过出液口2314流回接水盘31(冷凝水循环路径图4中以空心箭头示出)。与此同时，在风机24的带动下，湿空气通过进气口2311进入壳体231，在折流板233和隔板234的阻隔下，沿S型的折流通道往复流动，在流动过程中，与U型管充分接触实现与冷凝水之间的热交换而温度下降，热交换后的空气通过出气口2312流出壳体231(空气循环路径图4中以实心箭头示出)。
上述设置方式的优点在于：通过采用管壳式换热器，使得本申请的气液换热器23具有传热系数高、换热速度快、占用空间小、寿命 长等优点。通过在管壳式换热器内设置隔板234和折流板233，使得壳体231内部形成S型的折流通道，使得空气与换热管232充分接触，显著增加空气与换热管232的换热面积，从而大幅提高换热效果，进而降低蒸发器14的负担，提高系统的除湿效率。通过将进气口2311和出气口2312设置在壳体231的周侧且分别对应U型流道的一端，以及将进液口2313和出液口2314均设置于壳体231靠近U型管的自由端的端面上，使得空气在进入管壳式换热器后能够与换热管232最大程度的进行热交换，提高换热效果。通过将进气口2311开设于靠近U型的流道的上游端的壳体231上，出气口2312开设于靠近U型的流道的下游端的壳体231上，进液口2313开设于靠近U型管下游端的壳体231上，出液口2314开设于靠近U型管上游端的壳体231上，使得空气的流向与冷凝水的流向相反，实现空气与冷凝水之间的逆流换热，换热效果较佳。
进一步地，通过将回液口与液管33的自由端沿接水盘31的对角线设置，还能够避免冷凝水温度分布不均，提高冷凝水的换热效果。由于冷凝水为液体，压降较小，空气为气体，压降较大，因此将进气口2311的面积大于进液口2313和出液口2314的面积，出气口2312的面积大于进液口2313和出液口2314的面积，能够减小空气的压降，实现较好的流动换热效果。
实施例2
下面参照图3，对本申请的烘干系统的第二种实施方式进行描述。其中，图3为本发明的第二种实施方式中烘干系统的系统图。
如图3所示，在保持实施例1中其他结构设置不变的前提下，烘干系统还包括复叠换热器22，复叠换热器22具有第一进口221、第一出口222、第二进口223和第二出口224，第一进口221与第一出口222之间形成一个空气流道，第二进口223与第二出口224之间形成另一个空气流道，两个空气流道彼此交叉设置，从而能够交叉换热。第一进口221与湿空气出口211连通，第一出口222与气液换热器23的进气口2311连通，第二进口223与蒸发器14的出口连通，第二出口224与冷凝器12的进口连通。本申请对于复叠换热器22的具体结构形式不作限制，任何能够满足上述条件的换热器均可以作为复叠换热器22应用于本申请中。 例如，可以采用板翅式热交换器或转轮式热交换器作为本申请的复叠换热器22使用等。
按照图3所示方位，由湿空气出口211排出的高温湿空气在进入气液换热器23进行冷却前，首先通过复叠换热器22的第一进口221流入复叠换热器22的一个空气流道，流出蒸发器14的低温干空气通过复叠换热器22的第二进口223流入复叠换热器22的另一空气流道，两个空气流到内的空气进行热交换，从而高温湿空气的温度被降低，低温干空气的温度同时被升高(该过程是等量热交换)。然后，温度被降低后的湿空气继续向前流动到气液换热器23进行二次降温，与此同时，温度被升高后的干空气继续向前流动到冷凝器12进行二次升温。
可以看出，通过在烘干系统设置复叠换热器22，使得烘干系统能够同时提高蒸发器14与冷凝器12的换热效率，实现更高的除湿效率和更低的能耗。
具体地，湿空气在进入气液换热器23进行冷却前，首先通过复叠换热器22与流出蒸发器14的低温干空气进行热交换，其温度被大幅降低，低温干空气的温度同时被升高(该过程是等量热交换)，温度被降低后的湿空气继续向前依次流动到气液换热器23和蒸发器14进行二次和三次降温而达到露点温度以下，空气中的水分大幅析出，由于在此过程中湿空气不是直接送到蒸发器14进行热交换，而是先通过复叠换热器22与来自蒸发器14的低温干空气进行热交换，然后再经过气液换热器23进行二次热交换，最后才进入蒸发器14进行热交换，因此，到达蒸发器14的湿空气将比直接送到蒸发器14的湿空气的温度低很多，因而大幅度减轻了蒸发器14的负担，提高了除湿效率，经发明人反复试验、观测、分析和比较，在同时采用复叠换热器22和气液换热器23时，可实现整体除湿效率15％以上的显著提高。
与此同时，由于蒸发器14流出的低温干空气与湿空气进行了热交换，因此进入冷凝器12的空气温度也比不设置复叠换热器22而直接进如冷凝器12的温度高，这样经过冷凝器12排出再次进入干燥腔室21的空气温度也要比不设置复叠换热器22时要高，因此，复叠换热器22的设置也提高了进入干燥腔室21的空气的温度，相应地加快了衣物的烘干速度，使得干燥效率进一步提升，能耗进一步下降。
需要说明的是，上述优选的实施方式仅仅用于阐述本发明的原理，并非旨在于限制本发明的保护范围。在不偏离本发明原理的前提下，本领域技术人员可以对上述设置方式进行调整，以便本发明能够适用于更加具体的应用场景。
例如，在一种可替换的实施方式中，管壳式换热器的具体设置方式并非仅限于上述方式，本领域技术人员可以对其进行调整，只要其设置方式能够实现冷凝水与空气之间的热交换即可。比如，进气口2311、出气口2312、进液口2313和出液口2314的设置位置可基于实际产品进行调整，如进气口2311和出气口2312可以分别设置在侧壁的上部和下部，可以相背离设置也可以沿壳体231长度方向共线设置；换热管232的具体形式和数量可以进行调整，如还可以为直管或S型管等；折流板233和隔板234中的一个或全部都可以选择性地省略等。
再如，在另一种可替换的实施方式中，蒸发器14、冷凝器12和风机24的设置方式并非一成不变，在满足能够组成空气循环回路的前提下，本领域技术人员可以对上述部件的设置方式进行更改，这种更改并未偏离本申请的原理。比如，蒸发器14、冷凝器12和风机24中的一个或多个还可以直接设置在风管25内部。
再如，在另一种可替换的实施方式中，虽然上述实施方式中是以管壳式换热器进行阐述的，但是气液换热器23的实施方式不只限于此，本领域技术人员可以基于实际应用场景进行选择，即时其效果较管壳式换热器并不显著。比如，气液换热器23还可以板式换热器或套管换热器等，当使用套管换热器时，可以设置为空气走外管，冷凝水走内管，以兼顾流动换热效果。
当然，上述可以替换的实施方式之间、以及可以替换的实施方式和优选的实施方式之间还可以交叉配合使用，从而组合出新的实施方式以适用于更加具体的应用场景。
实施例3
本申请还提供了一种洗干一体机，该洗干一体机包括箱体(图中未标出)，箱体上设置有机门，箱体内设置有进水组件、驱动装置和洗涤筒组件，洗涤筒组件包括外筒和内筒，内筒能够容纳待洗涤衣物，进水组件能够将水源注入外筒中，驱动装置能够驱动内筒转动从而 完成对衣物的洗涤。该洗干一体机还包括上述实施例中所述的烘干系统，外筒上开设有湿空气出口211和干空气进口212，外筒、气液换热器23、蒸发器14、冷凝器12和风机24通过风管25连接组成空气循环回路。
通过在洗干一体机中设置上述的烘干系统，能够显著提升洗干一体机的烘干效率，降低烘干能耗。
本领域的技术人员能够理解，尽管在此所述的一些实施例包括其它实施例中所包括的某些特征而不是其它特征，但是不同实施例的特征的组合意味着处于本发明的范围之内并且形成不同的实施例。例如，在本发明的权利要求书中，所要求保护的实施例的任意之一都可以以任意的组合方式来使用。
至此，已经结合附图所示的优选实施方式描述了本发明的技术方案，但是，本领域技术人员容易理解的是，本发明的保护范围显然不局限于这些具体实施方式。在不偏离本发明的原理的前提下，本领域技术人员可以对相关技术特征作出等同的更改或替换，这些更改或替换之后的技术方案都将落入本发明的保护范围之内。

Claims (10)

  1. 一种烘干系统，其特征在于，所述烘干系统包括：
    冷媒循环回路，所述冷媒循环回路包括通过冷媒管连接的压缩机、冷凝器、节流元件和蒸发器；
    空气循环回路，所述空气循环回路包括通过风管连接的干燥腔室、气液换热器、所述蒸发器和所述冷凝器，所述干燥腔室具有湿空气出口和干空气进口，所述气液换热器具有进气口、出气口、进液口和出液口，所述进气口与所述湿空气出口连通，所述出气口与所述蒸发器的进口连通，所述蒸发器的出口与所述冷凝器的进口连通，所述冷凝器的出口与所述干空气进口连通；
    冷却循环回路，所述冷却循环回路包括通过液管连通的接水盘、水泵和所述气液换热器，所述接水盘设置于所述蒸发器的下方，用于收集冷凝水，所述进液口和所述出液口分别与所述接水盘连通，所述水泵设置于所述进液口/所述出液口与所述接水盘之间。
  2. 根据权利要求1所述的烘干系统，其特征在于，所述气液换热器为管壳式换热器，所述管壳式换热器包括壳体和设置于所述壳体内的换热管，所述进气口和所述出气口设置于所述壳体上且分别与所述壳体内部连通，所述进液口和所述出液口设置于所述壳体上且分别与所述换热管的两端连通。
  3. 根据权利要求2所述的烘干系统，其特征在于，所述管壳式换热器还包括折流板，所述折流板套设在所述换热管上，从而使得所述壳体内部形成有折流通道。
  4. 根据权利要求2所述的烘干系统，其特征在于，所述换热管为U型管，所述管壳式换热器还包括隔板，所述隔板沿所述壳体的长度方向固定于所述壳体内并将所述壳体内部分隔为截面为U型的流道，所述U型管对应设置于所述流道内。
  5. 根据权利要求4所述的烘干系统，其特征在于，所述进气口和所述出气口开设于所述壳体的周侧且分别对应所述U型的流道的一端；并且/或者
    所述进液口和所述出液口均设置于所述壳体靠近所述U型管的自由端的端面上。
  6. 根据权利要求4所述的烘干系统，其特征在于，沿所述空气的流动方向，所述进气口开设于靠近所述U型的流道的上游端的壳体上，所述出气口开设于靠近所述U型的流道的下游端的壳体上，所述进液口开设于靠近所述U型管下游端的壳体上，所述出液口开设于靠近所述U型管上游端的壳体上。
  7. 根据权利要求1所述的烘干系统，其特征在于，所述进气口的面积大于所述进液口和所述出液口的面积，所述出气口的面积大于所述进液口和所述出液口的面积。
  8. 根据权利要求1所述的烘干系统，其特征在于，所述烘干系统还包括复叠换热器，所述复叠换热器具有第一进口、第一出口、第二进口和第二出口，所述第一进口与第一出口之间形成的空气流道与所述第二进口与所述第二出口之间形成的空气流道能够交叉换热，
    其中，所述第一进口与所述湿空气出口连通，所述第一出口与所述进气口连通，所述第二进口与所述蒸发器的出口连通，所述第二出口与所述冷凝器的进口连通。
  9. 根据权利要求1所述的烘干系统，其特征在于，所述水泵设置于所述进液口与所述接水盘之间，所述进液口与所述水泵的出口之间通过液管连接，所述水泵的进口与所述接水盘之间通过一端为自由端的液管连接，所述接水盘上设置有回液口，所述出液口与所述回液口之间通过液管连通，所述自由端伸入所述接水盘并且所述自由端与所述回液口沿所述接水盘的对角线设置。
  10. 一种衣物处理设备，其特征在于，所述衣物处理设备包括权利要求1至9中任一项所述的烘干系统。
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