JP2017205651A - Washing and drying machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve reliability of a heat pump device by preventing blockage of a heat exchanger by lint, in a washing and drying machine mounting the heat pump device as a drying heat source.SOLUTION: A washing and drying machine includes a rotary drum, an outer tub for including the rotary drum, a heat pump device, a filter, a blower fan and a circulation air passage for connecting them. The heat pump device is constituted by a refrigerant circuit in which a compressor, a condenser for radiating heat of the refrigerant to the air, decompression means and an evaporator for absorbing heat from the air are connected sequentially. The washing and drying machine has a cooling part which becomes a temperature lower than a dew point temperature of the circulation air during a drying operation on an upstream of the evaporator of the heat pump device.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a washing / drying machine having a heat pump mounted on a drying heat source.

  The washing / drying machine performs washing to drying in one rotating tub. In a drum-type washing and drying machine, a drum as a rotary tub is installed to be rotatable around an axis that is horizontally or substantially inclined, and a series of steps of washing, rinsing, dewatering, and drying are performed by rotating the drum. Is what you do.

  As a heat source during the drying operation, a drying method using a heat pump device or a drying method using a heater is used. In order to dry moisture-containing clothing, it is necessary to continuously perform a drying cycle in which high-humidity air is removed from the drum and dehumidified and heated air is fed into the drum.

  In a washing and drying machine using a heat pump device as a drying heat source, a compressor, a heat exchanger (condenser) for heating the circulating air, a decompression means, and a heat exchanger (evaporator) for dehumidifying the circulating air are connected by piping. A refrigeration cycle sequentially connected and a blower for circulating the drying air are provided. In the refrigeration cycle, the refrigerant compressed to high temperature and high pressure by the compressor is sent to the heat exchanger (condenser) for heating to heat the air, and the air is dehumidified by the heat exchanger for dehumidification (evaporator) to low temperature and low pressure The refrigerant thus obtained is circulated through the compressor and compressed again, and the air blowing means dehumidifies the moisture from the clothes in the drum and dehumidifies the air with an evaporator and heats it with a condenser to reduce the humidity. The clothes are dried by blowing them again into the drum as air.

  In the drying process, air flows along with moisture evaporated from the clothing, and lint generated from the clothing. Relatively large lint is collected by a filter installed in the circulation air passage, but lint finer than the filter eyes passes through the filter, adheres to the heat exchanger of the heat pump device, closes the air passage, It has been found that the amount of heat exchanged into the air is reduced due to a decrease in air volume and an increase in thermal resistance, which causes a decrease in drying performance.

  There exists patent document 1 as an example of the background art of the washing-drying machine of the above technical fields. The washing and drying machine disclosed in Patent Document 1 dissipates heat of a water tank elastically supported in a housing, a rotary tank that is rotatably provided in the water tank and stores clothes, and a compressor and compressed refrigerant. A heat pump device and a fan connected to each other by a conduit so that the refrigerant circulates between a radiator to reduce the pressure of the high-pressure refrigerant and a heat absorber to which the reduced pressure and low-pressure refrigerant takes heat from the surroundings An air supply hose for supplying air heated by the radiator into the rotating tub by means and an exhaust hose for discharging the air supplied into the rotating tub by air blowing means to the outside of the water tank; The heat pump device includes a heat exchanger constituting the heat pump device and a means for cleaning the heat absorber. As a result, even if the stock solution of washing water, organic acid, or lint enters the blower circuit, it has a heat exchanger cleaning means, which reduces the air flow and heat exchange performance as a result of corrosion on the heat exchanger and the wind circuit. It is described that since it is difficult to be lowered, the reliability and durability of the heat pump device can be improved and excellent drying performance can be maintained.

JP 2005-224491 A

  In Patent Document 1 of the above-described prior art, a cleaning means is provided between the heat absorber (evaporator) and the radiator (condenser) in the air passage to eject the cleaning water to the heat absorber and the radiator. Supply tap water through a water supply hose or supply wash water from a dedicated tank to clean lint adhering to the heat exchanger, but deter adhesion of lint to the front of the heat exchanger Is not considered.

  Therefore, an object of the present invention is to improve the reliability and drying performance of a heat pump device by suppressing clogging of the heat exchanger due to lint in a washing dryer equipped with a heat pump device as a drying heat source.

In order to solve the above problems, a washing and drying machine according to the present invention includes a rotating drum, an outer tub containing the rotating drum, a heat pump device, a filter, a blower fan, and a circulation air path connecting them. In the washing and drying machine provided, the heat pump device is configured by a refrigerant circuit in which a compressor, a condenser that radiates heat of the refrigerant to the air, a decompression unit, and an evaporator that absorbs heat from the air are sequentially connected.
A cooling unit having a temperature lower than the dew point temperature of the circulating air during the drying operation is provided upstream of the evaporator of the heat pump device.

  According to the present invention, a cooling unit having a temperature lower than the dew point temperature of the circulating air during the drying operation is arranged upstream of the evaporator of the air passage from the outer tank to the heat pump device that is the drying heat source through the filter. Yes. By adopting such a configuration, lint accompanying the circulating air is collected along with condensation of moisture in the circulating air on the cooling unit, so that it is possible to suppress adhesion of lint to the front surface of the evaporator. Become. As a result, it is possible to improve the reliability of the heat pump device by preventing the blockage due to lint deposition on the front surface of the evaporator and the increase in ventilation resistance. Moreover, since the air volume during the drying operation can be ensured, it is possible to provide a washing and drying machine that achieves both reduced power consumption and improved drying performance by improving the dehumidifying performance.

It is a perspective view which cut | disconnects some housings of the washing-drying machine concerning the example of 1 embodiment of this invention, and shows an internal structure. It is a side view which shows the internal structure of the washing-drying machine concerning the example of 1 embodiment of this invention. It is a rear view which shows the internal structure of the washing-drying machine concerning the example of 1 embodiment of this invention. It is a schematic diagram which shows the structure of the heat pump apparatus concerning one embodiment of this invention. It is a schematic diagram which shows the structure of the heat pump apparatus of a common washing-drying machine. It is a schematic diagram which shows the refrigerant circuit of the heat pump apparatus concerning one embodiment of this invention. It is a schematic diagram which shows the refrigerant circuit of the heat pump apparatus concerning one embodiment of this invention. It is a schematic diagram which shows the refrigerant circuit of the heat pump apparatus concerning one embodiment of this invention. It is a schematic diagram which shows the refrigerant circuit of the heat pump apparatus concerning one embodiment of this invention. It is a schematic diagram which shows the refrigerant circuit of the heat pump apparatus concerning one embodiment of this invention. It is a schematic diagram which shows the structure of the cooling part and air path of the washing-drying machine concerning one embodiment of this invention. It is a schematic diagram which shows the structure of the circulation air path of the washing-drying machine concerning one example of embodiment of this invention.

  Example 1 according to the present invention will be described below. FIG. 1 is a perspective view showing an internal structure by cutting a part of the casing of the washing / drying machine 20 of this embodiment, FIG. 2 is a side view showing the internal structure of the washing / drying machine 20 of this embodiment, and FIG. 4 is a rear view showing the internal structure of the washing / drying machine 20 according to the embodiment, FIG. 4 is a schematic view showing the configuration of the heat pump apparatus of the washing / drying machine 20 according to this embodiment, and FIG. 5 shows the heat pump apparatus of a general washing / drying machine. It is a schematic diagram which shows a structure.

  In the washing / drying machine 20 of the present embodiment, the outer tub 101 is elastically supported by the suspension 104 on the base 105 of the washing / drying machine housing 100. A front surface of the outer tub 101 is opened and a rotatable drum 103 rotatably supported by a shaft is disposed. The rotating drum 103 is rotated by a driving force of a driving motor 107 provided on the rear surface of the outer tub 101. An opening 106 is formed on the front side of the washing / drying machine 20, and a door 111 that opens and closes the opening 106 is provided. The user can put the garment 200 into the rotary drum 103 from the opening 106 and take out the garment 200 that has been washed and dried.

In the upper part of the outer tub 101, detergent introduction means 108 is provided on the front left side as viewed from the front of the washing / drying machine 20, and a water supply unit 112 is installed on the rear left side. Further, a lint filter 90 and a blower fan 8 which are components of the drying means are installed on the upper part of the outer tub 101. The blower fan 8 is a centrifugal multiblade fan or a turbo blower.
In addition, an outlet 14 for circulating air into the rotary drum 103 is installed on the upper right side of the outer tank front cover 102 that constitutes the outer tank 101.

  The rear surface of the outer tub 101 is provided with a discharge port 15 for discharging the circulating air from the rotary drum 103, and the discharge port 15 is connected to the filter case 91 by an exhaust duct 73. The connection between the outer tub 101 and the duct is connected through a rubber bellows or the like in order to suppress transmission of vibration during operation.

  Next, the configuration and operation of the heat pump apparatus 1 will be described. FIG. 3 is a rear view showing the internal structure of the washing / drying machine 20 of the present embodiment, and shows the configuration of the refrigerant circuit 16 and the configuration of the circulation air path of the heat pump device 1. As shown in FIG. 4, the heat pump device 1 includes a compressor 2, a heat exchanger for heat radiation to air (condenser 3), a decompression device 5 (an expansion valve, etc.), and a heat exchanger for dehumidification of air (evaporation). 4), and a refrigerant circuit 16 in which these devices are sequentially connected by a refrigerant pipe 6 is accommodated in a resin casing 18. The refrigerant flows in the direction of the arrow indicated by R1 in the figure in the order of the compressor 2, the condenser 3, the decompression device 5, and the evaporator 4, and returns to the compressor again.

  Since the evaporator 4 and the condenser 3 constituting the heat pump device 1 exchange heat with air, a cross fin tube type heat exchanger attached to a laminated aluminum fin so as to penetrate the heat transfer tube is generally used. There are many cases. Hereinafter, the condenser and the evaporator are collectively referred to as a heat exchanger.

  The casing 18 of the heat pump apparatus 1 is configured to be separable into a lower casing (not shown) and an upper casing (not shown). The heat exchangers (evaporator 4 and condenser 3) are installed so as to be sandwiched between the upper casing and the lower casing so as to inhibit the air flowing to the side surface side, thereby forming a circulation air passage for the air.

  The compressor 2 is installed in the lower casing through vibration-proof rubber or the like. The refrigerant pipe 6 is connected to the heat radiation condenser 3 and the dehumidification evaporator 4 in a meandering state in order to prevent breakage due to propagation of rotational vibration of the compressor 2.

  As the compressor 2, a controllable compressor is used, and for example, a piston type, a rotary type, a scroll type or the like can be used. The rotation speed is variable from low speed to high speed by inverter control.

  Further, when the refrigerant returns to the compressor 2 in a liquid phase, reliability may be reduced due to poor lubrication on the sliding surface of the compressor 2. In order to suppress this, an accumulator (not shown) may be provided on the refrigerant suction side.

The high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the condenser 3 and is condensed and liquefied by releasing heat to the circulating air. The liquefied refrigerant is decompressed by an expansion valve (decompression device 5) adjusted to a predetermined opening, enters a low-temperature low-pressure gas-liquid two-phase state, and flows into the evaporator 4. It evaporates and vaporizes by absorbing heat from the circulating air. The vaporized refrigerant is sucked into the compressor 2 and compressed again by the compressor 2 to become a high-temperature and high-pressure gas refrigerant. In this way, the heat pump device 1 is formed.
A refrigerant is sealed in the refrigerant circuit 16, and for example, an HFC single refrigerant, an HFC mixed refrigerant, HFO-1234yf, HFO-1234ze, a natural refrigerant (for example, CO2 refrigerant), or the like can be used as the refrigerant.

  The heat pump apparatus 1 is installed on the lower part of the outer tub 101 and on the base 105 behind the washing / drying machine housing 100. The circulating air is discharged from the rotary drum 103 through the discharge port 15, passes through the lint filter 90, and then flows into the heat pump device 1 from the upper part of the outer tank 101 toward the lower part through the inlet-side flow path 70. The circulating air dehumidified and heated in the heat pump device 1 is connected to the blowing fan 8 from the outlet side flow channel 71 through which the circulating air flows from the lower part to the upper part of the outer tank 101 and is connected to the blowing fan 8. The air is blown into the rotary drum 103 by a blow-out port 14 provided at the upper front of 101.

  The evaporator 4 constituting the heat pump device 1 dehumidifies high-humidity air containing moisture evaporated from the clothing 200 in the rotary drum 103, and the condenser 3 determines the amount of heat absorbed by the evaporator 4 and the amount of heat of the compressor 2. Dissipates heat to the circulating air. In general, fin tube heat exchange increases the heat transfer area by cutting slits on the surface of laminated aluminum fins, processing creases, and closing the fin pitch, etc. Improves heat transfer performance. Further, the surface of the aluminum fin is subjected to a surface treatment such as a hydrophilic treatment so that moisture condensed on the fin surface can be easily washed away.

  During the drying operation, the evaporator 4 is controlled so as to be equal to or lower than the dew point temperature of the circulating air. Therefore, moisture in the circulating air is condensed and attached to the surfaces of the fins constituting the evaporator 4.

  If the condensed dehumidified water does not flow down to the lower part of the evaporator 4 and is held between the fin slits or between the fins, that is, if the drainage is poor, ventilation resistance is generated for the circulating air, and the fan power There is a concern that the water film becomes a thermal resistance and the heat transfer performance is lowered. Here, the ventilation resistance is a pressure gauge provided before and after the heat exchanger (evaporator 4 and condenser 3), and the pressure difference of the air passing through the heat exchanger (evaporator 4 and condenser 3) is measured. Is.

  As shown in FIG. 3, the circulating air is discharged from the discharge port 15 on the back surface of the outer tub 101 and reaches the lint filter 90 via the exhaust duct 73. In the lint filter 90, lint generated from the clothing 200 during washing and drying is collected on the mesh of the lint filter 90. However, it is difficult to remove all the lint in the lint filter 90, and the fine lint that has passed through the filter mesh reaches the heat pump device 1 through the inlet-side flow path 70, and is located in the evaporator upstream of the air path. 4 may adhere to the front surface or between the fins. If the lint adhering to the evaporator 4 accumulates, the air flow flowing to the heat exchanger (evaporator 4 and condenser 3) is obstructed. Since the pressure loss of the road increases, there are problems such as an increase in power consumption because the air volume decreases and the drying time becomes longer.

  Therefore, a structure is provided in which a cooling unit 17 is provided on the upstream side of the evaporator 4 of the heat pump device 1 of the present embodiment so as to have a temperature lower than the dew point temperature of the circulating air during the drying operation.

  Since the temperature of the cooling unit 17 is set lower than the dew point temperature of the circulating air, the water in the circulating air is condensed in the form of water droplets or a liquid film on the surface of the cooling unit 17. Since the fine lint that has flowed with the circulating air is collected in contact with the water droplets or the liquid film on the surface of the cooling unit 17, it is suppressed from flowing into the evaporator 4.

  With the above-described configuration, the lint flowing along with the circulating air can be collected on the cooling unit 17 and the inflow to the heat exchanger (evaporator 4 and condenser 3) can be suppressed. And lint accumulation between the fins can be prevented. Therefore, the decrease in circulating air volume due to fin blockage and the increase in fan input for maintaining the air volume can be suppressed, and further, the increase in drying operation time can be suppressed. It can suppress, and the effect which aims at energy saving can be acquired.

  The supply of cold heat to the cooling unit 17 is performed by disposing the refrigerant circuit 16 of the heat pump device 1 up to the place where the cooling unit 17 is installed. Except for the case where the refrigerant pipe 6 functions as the cooling unit 17, in order to efficiently transmit the cold heat from the refrigerant pipe 6 to the cooling unit 17, the refrigerant pipe 6 and the heat transfer surface need to be in thermal contact. As a thermal contact method, a method of brazing the cooling unit 17 and the refrigerant pipe 6 or a material having high thermal conductivity between the cooling unit 17 and the refrigerant pipe 6 is reduced to reduce the contact thermal resistance. Examples of the method include, but are not limited to, a method.

  Moreover, since the surface of the cooling unit 17 collects lint by water droplets condensed on the surface, a structure that easily retains water droplets is desirable. For example, it becomes easy to generate droplets on the surface of the cooling unit 17 by performing hydrophilic treatment on the surface. By adopting such a configuration, when the droplet collecting lint grows to a certain size or more, it falls down by its own weight, and the water droplet containing lint is removed and discharged from the surface of the cooling unit 17. become.

  As another example of the structure of the cooling unit 17, a latent heat storage material (not shown) is arranged around the refrigerant pipe 6 of the cooling unit 17, and the refrigerant pipe, the latent heat storage material, and the cooling unit 17 are in thermal contact with each other. The configuration is as follows. Thus, by setting it as the structure by which cold heat is supplied to the cooling part 17 from a latent heat storage material, even when supply of the cold heat from the refrigerant | coolant piping 6 to the cooling part 17 stops, latent heat is in operation of the heat pump apparatus 1. The cooling unit 17 can maintain a low temperature for a certain period of time by the cold energy stored in the heat storage material.

  Moreover, frost and ice can be generated on the surface of the cooling unit 17 by controlling the surface temperature of the cooling unit 17 to be lower than the refrigerant temperature of the evaporator 4, for example, 0 ° C. or less.

  With this configuration, lint in the circulating air is collected in contact with the frost (ice), and the frost (ice) grows in a state where the lint is confined, so that the collected lint is in the circulating air. It can be prevented from flowing out.

  Further, the frost (ice) containing lint melts and flows down by its own weight when the operation of the heat pump device 1 is stopped and the cooling power supply to the cooling unit 17 is finished, and is similar to the dehumidified water of the evaporator 4. It is discharged from the drainage part 18a.

  Furthermore, by providing water supply means (not shown) from the water supply unit 112 to the cooling unit 17 in the cooling unit 17, it becomes possible to generate frost (ice) on the surface of the cooling unit 17, and effectively on the cooling unit 17. You can capture lint.

  In addition, by supplying water from the water supply unit 112 to the cooling unit 17, it is possible to wash away lint attached on the cooling unit 17 with water. Since the lint removed from the cooling unit 17 is discharged from the casing 18 of the heat pump device 1 by the dehumidifying water discharging means 18 a in the same manner as the dehumidified water of the evaporator 4, the amount of lint adhering to the front surface of the evaporator 4 Can be suppressed. The fluid supplied from the water supply means 112 to the cooling unit 17 may be any fluid suitable for the purpose of washing away lint attached to the surface, such as tap water or water in which detergent is dissolved.

  6 to 9 are schematic views showing a refrigerant circuit of a heat pump device according to an embodiment of the present invention in which a cooling unit 17 is provided.

  In FIG. 6, the refrigerant circuit that reaches the cooling unit 17 branches after flowing in two directions, a path that flows to the evaporator 4 through the condenser 3 and a path that flows to the cooling unit 17, and then merges. The refrigerant that has flowed to the evaporator 4 via the expansion valve 5a passes through the valve V1, and the refrigerant that has flowed to the cooling unit 17 via the expansion valve 5b passes through the valve V2. Since the cooling unit 17 and the evaporator 4 are partitioned by the expansion valves (5a, 5b) and the valves (V1, V2), respectively, the cooling unit 17 and the evaporator 4 are used together, or one of them is used. Therefore, the operation pattern can be changed as necessary.

  For example, when the cooling unit 17 and the evaporator 4 are used in combination, the circulating air can be dehumidified in the evaporator 4 while collecting the lint by the cooling unit 17.

  Further, as in the above-described embodiment, in the case where the latent heat storage material disposed in the cooling unit 17 stores the cold, only the cooling unit 17 may be used without using the evaporator 4.

  Further, the refrigerant can be temporarily stored in the refrigerant pipe on the unused side by opening / closing the expansion valves (5a, 5b) and the valves (V1, V2).

  In addition, the refrigerant circuit of FIG. 7 can be switched between a refrigerant path that reaches the evaporator 4 after passing through the cooling section 17 and a refrigerant path that bypasses the cooling section 17. By setting it as such a structure, after carrying out cold storage to the latent-heat storage material arrange | positioned at the cooling part 17 like the Example mentioned above, the driving | operation which isolate | separates the cooling part 17 and dehumidifies is attained.

  In the refrigerant circuit of FIG. 8, the cooling unit 17 is disposed in the downstream of the evaporator 4. With such a configuration, since the refrigerant flows through the cooling unit 17 following the evaporator 4 at the same flow rate, the evaporation pressure is reduced and the evaporation temperature is lowered due to an increase in refrigerant pressure loss. Thereby, it is possible to operate with the refrigerant temperature of the cooling unit 17 lower than the refrigerant temperature of the evaporator 4.

  Furthermore, the refrigerant circuit of FIG. 9 is an example in which the evaporator 4a, the cooling unit 17, and the evaporator 4b are arranged in this order. With such a configuration, since the refrigerant flows through the cooling unit 17 following the evaporator 4a at the same flow rate, the evaporation pressure is reduced and the evaporation temperature is lowered due to an increase in the pressure loss of the refrigerant. Thereby, the driving | running which made the refrigerant | coolant temperature of the cooling part 17 lower than the refrigerant | coolant temperature of the evaporator 4a is attained. Further, by performing heat exchange with the circulating air by the evaporator 4b, the degree of superheat of the refrigerant is increased at the inlet of the compressor 2, and the refrigerant is prevented from flowing into the compressor 2 in the liquid phase. It becomes possible to protect.

  With the above-described configuration, it is possible to effectively remove lint in the cooling unit 17 and dehumidify the circulating air, and fan power by preventing lint accumulation on the heat exchanger (evaporator 4 and condenser 3). Increase in energy consumption can be suppressed, and energy saving during drying operation can be achieved.

  FIG. 10 schematically shows a refrigerant circuit of a heat pump device according to an embodiment of the present invention. FIG. 10 a shows the refrigerant flow during the drying operation, and FIG. 10 b shows the refrigerant flow when the refrigerant circuit is switched by the four-way valve 30.

  The refrigerant circuit for the defrosting operation shown in FIG. 10 b passes through the compressor 2 and the four-way valve 30, branches in two directions of the cooling unit 17 and the evaporator 4, and then merges and passes through the condenser 3 and the four-way valve 30. Thus, the configuration returns to the compressor 2. Since the refrigerant flow is reversed by the four-way valve 30, high-temperature and high-pressure gas refrigerant flows into the cooling unit 17 and the evaporator 4 to function as a condenser. For this reason, the generated frost and ice on the cooling unit 17 are melted, and water droplets on the surface of the evaporator 4 are dried. By performing this defrosting operation, the cooling unit 17 and the evaporator 4 at the end of the drying operation are in a dry state, and an effect of suppressing odor generation due to water droplets and impurities remaining on the heat transfer surface is obtained.

  FIG. 10 shows a configuration in which the four-way valve 30 is installed in the refrigerant circuit shown in FIG. 6 as an example, but the structure is not limited. For example, the four-way valve 30 is added to the refrigerant circuit in FIGS. The arrangement may be the same, and the same effect can be obtained.

  As described above, the circulating air discharged from the rotating drum 103 flows with lint generated from the clothing 200 as the drying progresses. The finned tube heat exchanger used in the heat pump device 1 has a structure in which a large number of aluminum fins are stacked. Therefore, if lint is deposited on the front surface of the evaporator 4 or between the fins, the air path resistance of the circulating air As a result, the exchange heat quantity may be reduced. In other words, effective capture of lint by the lint filter 90 is important for the heat pump apparatus 1. However, if the filter mesh is made too fine to collect the lint in the lint filter 90, the air path resistance increases due to the blockage of the lint filter 90, the power of the fan increases, and the energy saving performance decreases. There is a concern that the air volume will decrease.

  In order to solve the above-described problems, the washing / drying machine 20 of the present embodiment is configured to install the cooling unit 17 in the exhaust duct 73. With such a configuration, the circulating air exhausted from the rotary drum 103 is condensed on the cooling unit 17 and flows into the lint filter 90 leaving the accompanying lint in the condensed water. Therefore, since the amount of lint flowing into the lint filter 90 is suppressed, an increase in ventilation resistance due to lint deposition can be prevented, and an increase in power consumption of the fan can be suppressed.

  Furthermore, if water supply means (not shown) from the water supply unit 112 provided at the upper part of the outer tub 101 to the inlet-side flow path 70 is provided, it becomes possible to wash out lint attached to the cooling unit 17 with water. .

  In addition, by supplying water from the water supply unit 112 to the cooling unit 17, frost (ice) can be generated on the surface of the cooling unit 17, and lint can be effectively captured on the cooling unit 17.

  With the above-described configuration, the lint flowing along with the circulating air can be collected on the cooling unit 17 and can be prevented from flowing into the heat exchanger (evaporator 4. condenser 3). And lint accumulation between the fins can be prevented. Therefore, an increase in fan input can be suppressed, and an increase in power consumption during the drying operation can be suppressed, and an effect of energy saving can be obtained.

  A surface treatment is applied to the inner surface of the inlet-side flow path 70 of the heat pump device 1 so that the lint that has passed through the filter mesh is likely to adhere to the inner surface of the inlet-side flow path 70, and the water supply provided in the upper part of the outer tub 101 If water supply means (not shown) is provided from the unit 112 to the inlet-side channel 70, the lint attached to the inner surface of the inlet-side channel 70 can be washed away with water.

  Furthermore, since the above-mentioned water supply means can supply water to the cooling unit 17, it is possible to effectively wash away the lint attached to the cooling unit 17.

  The lint removed from the inner surface of the inlet-side channel 70 is discharged from the casing 18 of the heat pump device 1 by the drain discharge means (not shown) together with the dehumidified water of the evaporator 4. The amount of lint that adheres can be suppressed. The fluid supplied from the water supply means 112 to the inlet-side flow path 70 is suitable for use in washing away lint attached to the inner surface of the inlet-side flow path 70, such as tap water or water in which detergent is dissolved. I just need it.

  FIG. 11: has shown the schematic diagram which shows the structure of the cooling part and air path of the washing-drying machine concerning one example of embodiment of this invention.

  FIG. 11 a shows an example in which the cooling unit 17 is installed in the exhaust duct 73. In the figure, the cooling unit 17 is installed at a bent portion immediately after the circulating air is discharged from the outer tub 101 and at a bent portion toward the lint filter 90. With such a configuration, the circulating air is easily brought into contact with the cooling unit 17 because the flow direction changes depending on the bent portion. Further, moisture and lint condensed in the cooling unit 17 flow down in the exhaust duct 73 by gravity, flow into the outer tub 101, and are discharged from the drain hose 110.

  With the above configuration, it is possible to effectively remove lint and dehumidify the circulating air in the cooling unit 17, and suppress an increase in ventilation resistance of the lint filter 90 due to lint accumulation, thereby suppressing a decrease in circulating air volume. Therefore, an increase in power consumption due to an increase in the drying operation time can be suppressed.

  FIG. 11 b shows an example in which the cooling unit 17 is installed at the inlet of the heat pump device 1. In the drawing, the cooling unit 17 is installed at a bent portion of a circulation air path from the inlet-side channel 70 toward the heat pump device 1. With such a configuration, the circulating air changes its direction of flow due to the bent portion, so that it easily comes into contact with the cooling portion 17. Also, moisture and lint condensed in the cooling portion 17 flow down due to gravity and are thus heated by the heat pump device 1. Into the casing 18 and discharged from the drainage portion 18a.

  FIGS. 11 c to 11 d show an example in which the cooling unit 17 is installed in the inlet-side flow path 70. In the figure, the cooling unit 17 is disposed at a substantially central portion in the longitudinal direction of the inlet-side channel 70.

  In FIG. 11 c, since the cooling unit 17 is installed in the inlet-side flow path 70 in the shape of a twisted tape, the circulating air flows along the surface of the cooling unit 17 with swirling, and dew condensation occurs on the surface of the cooling unit 17. The lint is then collected in droplets. The condensed moisture and lint flow along the cooling unit 17, flow down the inner surface of the inlet-side flow path 70, flow into the casing 18 of the heat pump device 1, and are discharged from the drainage unit 18 a.

  In FIG. 11d, the cooling part 17 is formed radially. Since the circulating air passes through the flow path divided by the cooling unit 17, condensation occurs on the surface of the cooling unit 17, and lint is collected in droplets. The condensed moisture and lint flow along the cooling unit 17, flow down the inner surface of the inlet-side flow path 70, flow into the casing 18 of the heat pump device 1, and are discharged from the drainage unit 18 a.

  With the above configuration, it is possible to effectively remove the lint in the cooling unit 17 and dehumidify the circulating air, suppress the inflow of the lint to the heat pump device 1, and perform lint deposition on the front surface of the evaporator 4. Increase in ventilation resistance can be suppressed. Accordingly, it is possible to prevent a reduction in the air volume during the drying operation and an increase in the power consumption due to the air volume maintenance, so that an effect of energy saving can be obtained.

  The washing / drying machine 20 of this embodiment includes a control device 13. The control device 13 senses the capacity of the garment 200 put into the rotating drum 103 at least at the start of the washing operation, the drying operation, or the washing / drying operation, and determines the amount of detergent to be put in and the operation time based on the determination value. It is determined and displayed on the display, but during operation, the capacity is sensed again to review the operation time, select the optimal operation time and operation process according to the clothing capacity, and dry consumption An increase in the amount of electric power can be suppressed.

  Furthermore, the heat pump device 1 includes a sensor that detects the temperature of the refrigerant flowing through the heat exchanger (the condenser 3 and the evaporator 4). FIG. 3 shows an example in which temperature sensors T1, T2, and T3 are installed in the refrigerant pipe 6. Usually, in the refrigeration cycle, a pressure sensor and a temperature sensor are installed in the refrigerant pipe 6 and the heat exchanger (the condenser 3 and the evaporator 4) in order to grasp the operation state. As an example, the sensors are installed at the suction side, the discharge side, the inlet / outlet of the heat exchanger (evaporator 4 and condenser 3), before the expansion valve (decompression device 5), etc. A refrigeration cycle is controlled by estimating a Mollier diagram representing the state. In the refrigerant circuit 16 of the present embodiment, the performance of the refrigeration cycle is estimated by a temperature sensor, but a configuration in which a pressure sensor is attached may be used. If the pressure data can be used by the control device 13, it is possible to control the coefficient of performance (COP) of the refrigeration cycle to be optimal, and it is possible to reduce power consumption during the drying operation.

  The circulating air during the drying operation is discharged from the rotating drum 103, passes through the lint filter 90, is dehumidified and heated by the heat pump device 1, and is blown again into the rotating drum 103 by the blower fan 8. The washing / drying machine 20 of the present embodiment includes a temperature and humidity sensor (not shown) in order to monitor the state of the circulating air. By grasping temperature and humidity data at the outlet 14 to the rotating drum 103 and the outlet 15 from the rotating drum 103 during the drying operation, an approximate evaporation amount of moisture from the clothing 200 is estimated, and the clothing 200 is dried. By estimating the state, it is possible to optimally set the drying operation time. For this reason, the amount of power consumption during the drying operation can be suppressed and energy saving can be obtained.

  From the temperature and humidity data of the circulating air, the dew point temperature of the circulating air can be calculated. As an operating condition of the refrigeration cycle of the heat pump device 1, if the dew point temperature of the circulating air at the heat pump inlet can be grasped, the refrigerant temperature flowing through the evaporator 4 is controlled to be lower than the dew point temperature of the circulating air. Dehumidification performance can be improved. By controlling the temperature of the cooling unit 17 to be lower than the refrigerant temperature of the evaporator 4, it is possible to collect the lint that flows accompanying the circulating air by the cooling unit 17.

  Further, the control device 13 controls the opening degree of the expansion valve 5 of the heat pump device 1, the rotation speed of the compressor 2, and the rotation speed of the blower fan 8 according to the operation process determined based on the capacity of the clothing 200. The amount of water to be evaporated from the garment 200 during the drying operation is estimated from the type and weight of the garment 200 and the weight of the garment after dehydration. In order to evaporate the estimated moisture from the clothing 200, it is necessary to optimally control the condensation temperature of the heat pump device 1, the evaporation temperature, and the circulation amount of the refrigerant.

  Usually, the condensing temperature is set higher than the temperature of air blown into the rotating drum 103, and the evaporation temperature is set below the dew point temperature of the air blown out from the rotating drum 103. At this time, if the evaporation temperature is too low, dehumidification of the air is promoted, but the circulating air is cooled more than necessary, and the amount of heating in the condenser 3 may be insufficient. In such a case, it may be possible to increase the refrigerant circulation amount to increase the condensation temperature. However, since the power consumption of the compressor 2 increases at the same time, the power consumption for drying increases and the drying efficiency increases. Will fall.

  In order to reduce the power consumption during the drying operation as described above, it is effective to reduce the power consumption of the compressor 2 occupying most of the power consumption in the heat pump device 1 and the power consumption of the blower fan 8. Thus, by optimizing the drying operation time, it is possible to obtain the effect of reducing the power consumption during the drying operation and saving energy.

  Further, as shown in FIGS. 1 to 3, the length of the air path from the blower fan 8 to the rotary drum 103 to the blowout port 14 is shortened, so that the high-speed, high speed can be obtained from the blowout port 14. It is possible to blow air of air volume on clothes, and there is an effect of obtaining high finishability during the drying operation.

  In addition, it is possible to make a short air path from the blowout duct 74 to the air outlet 14 that constitutes the air path through which the air having a high flow velocity boosted by the blower fan 8 flows, and an increase in pressure loss can be suppressed. For this reason, since the power consumption of the blower fan motor 81 can be reduced, it is possible to have high energy saving performance with reduced power consumption during the drying operation.

  Here, the position of the air outlet 14 is not necessarily the upper part on the front side. For example, when the air outlet 14 is provided on the back side of the rotary drum 103, the area of the discharge port 14 can be easily increased, so that the drying performance can be enhanced by drying with a large air volume. Further, in the case of a washing / drying machine in which the rotary drum 103 is disposed at an angle, the clothes 200 are likely to gather behind the rotary drum 103, and therefore, the effect of promoting the agitation (replacement) of the clothes by setting the discharge port 14 on the back side. Can also be obtained. However, when the air outlet 14 is provided on the back side, it is necessary to install a slit-like or mesh-like cover or the like. In the case where it is important to blow the air, it is preferable to provide the discharge port 14 on the front side.

  In the initial stage of the drying operation, operating only the blower fan 8 to circulate the air has an effect of loosening the garments 200 in a state of sticking to the inner wall surface of the rotary drum 103 or entangled after dehydration. Since the circulating air easily hits the clothing 200, the drying efficiency is improved. As described above, since the drying operation is performed efficiently, an increase in power consumption during the drying operation can be suppressed and an effect of energy saving can be obtained.

  FIG. 12 is a schematic diagram showing the configuration of the circulation air path of the washing and drying machine of the present embodiment. In the figure, the E circulating air passage 75 for returning the circulating air to the rotating drum 103 via the heat pump device 1 is indicated by a solid line, and the F circulating air passage 76 for returning the circulating air to the rotating drum 103 by bypassing the heat pump device 1 is indicated by a broken line. Is shown. The inside of the frame surrounded by the alternate long and short dash line schematically shows the inside of the washing and drying machine main body 100, the left side corresponds to the front side of the washing and drying machine housing, and the right side corresponds to the back side.

  As described above, with the configuration including the two circulation air passages, in addition to the drying operation using the heat pump device 1, the air circulation operation using the F circulation air passage 76 bypassing the heat pump device 1 can be performed. It becomes possible.

  As an example of the operation pattern, it is assumed that the circulation operation using the F circulation air passage 76 for a predetermined time is performed before the drying operation is started. In the circulation operation using only the F circulation air passage 76, the pressure loss of the air passage is small as compared with the E circulation air passage 75 passing through the heat pump device 1, so that an operation with an increased air volume is possible. When the air flow is increased and the circulating operation is continued, the heat generated by the blower fan motor 81 is transmitted to the air, and the circulating air temperature tends to gradually increase.

  By performing the operation using only the F circulation air passage 76 at the end of the dehydration, there is an effect of loosening the garment 200 attached to the inner surface of the rotary drum 103 by the dehydration and an effect of increasing the temperature of the garment 200. Due to the above-described effects, the evaporation of moisture from the garment 200 is promoted during the drying operation using the E circulation air passage 75, and the drying efficiency can be improved. For this reason, there is an effect of achieving energy saving while suppressing an increase in the amount of dry power consumption, and an effect of obtaining high finishing performance at the time of drying operation by blowing high-speed, high air volume air on clothes.

  In addition, in FIG. 12, the E circulation air passage 75 and the F circulation air passage 76 are shown as independent air passages, but the structure is not limited, and the air passage from the rotary drum 103 to the lint filter 90, The air path from the blower fan 8 to the rotating drum 103 may be shared. When the air path is shared, a separate air path closing means (not shown) and an opening means (not shown) are required, but the air path configuration can be made compact.

  Further, as described above, the circulating air is bypassed by the heat pump device 1, the air flow sucked by the blower fan 8, and the two air sucked by the blower fan 8 after being dehumidified and heated via the heat pump device 1. In the case of a configuration in which the air flow is branched, the air passage that passes through the heat pump device 1 out of the two air passages passes through the heat exchanger (evaporator 4 and condenser 3). Ventilation resistance increases. For this reason, a lot of circulating air flows in the flow path that bypasses the heat pump device 1.

  At the start of the drying operation, the startup characteristic of the heat pump device 1 affects the drying operation efficiency. Therefore, when the compressor 2 is started, the air flow of the blower fan 8 may be reduced. By providing an air passage that bypasses the heat pump device 1 as described above, it becomes possible to reduce the amount of air flowing to the heat pump device 1 while keeping the operation state of the blower fan 8 constant, and the same effect as the warm-up operation can be obtained. I can do it.

  Thus, by making the operation start of the heat pump device 1 faster, the drying operation time can be optimally controlled, and an increase in power consumption during the drying operation can be suppressed, and an effect of energy saving can be obtained.

  In addition, when the air path configuration bypassing the heat pump device 1 is used, the lint contained in the circulating air can be efficiently collected by the lint filter 90. Therefore, by using the cooling unit 17 disposed in the exhaust duct 73 in a process in which a large amount of lint is generated during the drying operation, lint in the circulating air is captured on the cooling unit 17 before flowing into the lint filter 90. Be collected.

  By adopting such a configuration, it becomes possible to lengthen the time until the lint filter 90 is blocked and the ventilation resistance is increased, leading to a reduction in fan power during the drying operation, thus saving energy during drying. effective.

  Further, it is possible to select a course for drying the clothes 200 in a short time according to the user's selection. In the course described above, the rotation speed of the compressor is increased in order to set the temperature at which the circulating air is blown into the rotary drum 103 to be high, and the heat pump device 1 is warmed up during the dehydration operation. If such an operation is performed, the input of the compressor 2 may increase, but the dry state of the garment 200 is estimated from the change in the temperature and humidity of the circulating air circulating through the rotary drum 103 and the heat pump device 1. By doing this, it is possible to determine the drying operation time, and to suppress a significant increase in power consumption and excessive heating of the garment 200. With the above-described configuration, it is possible to realize a drying operation that saves energy.

  Further, during the dehydration operation, the moisture dehydrated from the clothing 200 and the high-humidity air in the rotary drum 103 are discharged from the drain hose 110 to the outside of the washing dryer 20. At this time, by operating the heat pump device 1, it is possible to cause the humid air to be condensed on the cooling unit 17 and discharged.

  From the above operation, moisture can be efficiently removed from the circulating air during the drying operation, and the effect of shortening the time during the drying operation and suppressing a significant increase in power consumption can be obtained.

  In addition, a circulating air outlet 14 is provided in the outer tank front cover 102, and a circulating air outlet 15 is provided above the rotating shaft of the rotating drum 103 on the back surface of the outer tank 101. The position is set to a position close to the rotation center axis of the rotary drum 103 with respect to the position of the air outlet 14.

  With such a configuration, the airflow flowing from the blower outlet 14 into the rotary drum 103 is blown out diagonally to the left when viewed from the front of the washer / dryer 20. By providing the circulating air discharge port 15 on the opposite side of the back surface, it is possible to suppress the blown air from flowing as a shortcut to the discharge port 15. With the above configuration, by blowing high-speed and high-pressure air onto the garment 200 in the rotary drum 103, it is possible to achieve a high dry finish with less wrinkles during drying. In addition, when the clothes 200 and the dry air easily come into direct contact with each other, evaporation of moisture from the clothes 200 is promoted. Since the air containing moisture evaporated from the clothes 200 can be easily introduced into the heat pump device 1 from the discharge port 15, an operation with improved drying efficiency is possible. Therefore, it is possible to save energy by suppressing power consumption during the drying operation.

  In each of the above-described embodiments, the drum-type washing / drying machine has been described as an example of the application apparatus. It can also be applied to a dryer having only a drying function.

1 ... heat pump device,
2 ... Compressor,
3 ... Condenser,
4 ... Evaporator,
4a ... evaporator, 4b ... evaporator,
5 ... decompression device,
5a ... decompression device, 5b ... decompression device,
6 ... refrigerant piping,
70: Inlet side channel 71: Outlet side channel,
72 ... Blower inlet duct,
73 ... exhaust duct,
74 ... Blowout duct,
75 ... E circulation air passage 76 ... F circulation air passage 8 ... Blower fan,
81 ... Blower fan motor,
90 ... Lint filter,
91 ... Filter case,
10 ... Branch part of the air passage 11 ... Heat transfer tube,
12 ... Fins,
13 ... Control device,
14 ... Blowout outlet,
15 ... discharge port,
16 ... Refrigerant circuit 17 ... Cooling unit 18 ... Casing 18a ... Drainage unit 20 ... Washing and drying machine,
30 ... Four-way valve 100 ... Washer / dryer housing,
101 ... Outer tank,
102 ... outer tank front cover,
103 ... Rotating drum 104 ... Suspension,
105 ... Base,
106 ... opening,
107: Drive motor,
108: Detergent charging means,
109 ... Drain valve,
110 ... Drain hose,
111 ... door,
112 ... water supply unit,
200 ... clothes,
T1, T2, T3 ... Temperature sensors V1, V2 ... Valves

Claims (5)

In a washing and drying machine provided with a rotating drum, an outer tub enclosing the rotating drum, a heat pump device, a filter, a blower fan, and a circulation air passage connecting them,
The heat pump device is composed of a refrigerant circuit in which a compressor, a condenser that radiates heat of the refrigerant to the air, a decompression unit, and an evaporator that absorbs heat from the air are sequentially connected.
A washing and drying machine, wherein a cooling unit having a temperature lower than a dew point temperature of circulating air during a drying operation is provided upstream of the evaporator. In the washing and drying machine according to claim 1,
The washing / drying machine according to claim 1, wherein the cooling unit is disposed in one or both of a path from the outer tub to the filter and a path from the filter to the evaporator. In the washer / dryer according to claim 1,
The washing / drying machine, wherein a surface temperature of the cooling unit is lower than a surface temperature of the evaporator. In the washing and drying machine according to claim 1 to 3,
The heat pump device includes the compressor, a plurality of heat exchangers, the cooling unit, a plurality of decompression means, and a plurality of valves, and constitutes a refrigerant circuit capable of switching between the cooling unit and the heat exchanger. Features a washing dryer. In the washing and drying machine according to claim 1 to 4,
The washing / drying machine is characterized in that the cooling unit is arranged in a state where condensed water can flow down due to gravity.

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