JP2018038605A - Clothes dryer - Google Patents

Abstract

PROBLEM TO BE SOLVED: To perform proper control of a driving frequency at start-up of a compressor and to prevent causing of deterioration of drying performance, in a clothes dryer including a heat pump.SOLUTION: A clothes dryer includes: a drying chamber in which clothing is accommodated; a circulation air passage for circulating and supplying drying air to the drying chamber; a blower for blowing the drying air in the circulation air passage; a heat pump including a compressor, a condenser, an evaporator and a decompression device, and for dehumidifying and heating the drying air; a refrigerant temperature sensor for detecting a temperature of a refrigerant in the heat pump; and a control device for executing a drying operation by controlling the blower and the heat pump. The control device variably controls an increasing speed based on the detection temperature of the refrigerant temperature sensor, when increasing a driving frequency of the compressor to a target frequency at the start-up of the compressor.SELECTED DRAWING: Figure 1

Description

  Embodiments described herein relate generally to a clothes dryer.

  For example, in a drum-type clothes dryer, there is a drying mechanism including a circulation air passage for circulatingly supplying dry air into a drum (water tank) in which clothes are stored, and a blower and a heat pump (for example, Patent Document 1). A heat pump is configured by connecting a compressor, a condenser, a throttle valve, and an evaporator in a closed loop with a refrigerant pipe, and the wind flowing through the circulation air path is dehumidified through the evaporator and then heated by the condenser. It becomes dry and dry, and is used for drying clothes. The compressor is driven by an inverter motor having a variable driving frequency (rotational speed), and is inverter-controlled by a command from a control device.

  The heat pump is used in a predetermined temperature range in order to prevent problems such as a compressor failure caused by the internal refrigerant becoming high temperature and pressure. In Patent Literature 1, when the compressor is driven at a relatively high frequency (90 Hz) and the temperature detector that detects the outside air temperature detects a high temperature (35 ° C. or higher), the drive frequency of the compressor is normal. Is controlled to be lowered to 35 Hz. Thereby, it can suppress that a refrigerant | coolant becomes high temperature and high pressure more than necessary, and can avoid stopping a compressor temporarily.

Japanese Patent Application Laid-Open No. 2014-18452

  Generally, in the heat pump as described above, when the drying operation is started and the compressor is started, the compressor driving frequency is kept constant until the compressor reaches the target driving frequency (rotation speed). Control to increase at an ascending speed (acceleration) is performed. For example, the compressor is raised from a stopped state (0 Hz) to 40 Hz over 1 minute. In this case, if the drive frequency is increased too rapidly, the refrigerant becomes hot more than necessary, causing a situation where the compressor is temporarily stopped. However, if too much emphasis is placed on preventing abnormal temperature rise of the refrigerant, the drive frequency may start up more slowly than necessary when starting the compressor, or the drive frequency may be set lower than necessary. Happens. For this reason, there is an adverse effect that rather lowers the drying performance.

  In addition, when the temperature of the refrigerant in the evaporator becomes too low (for example, −10 ° C. or lower) in the heat pump driving state, condensation or freezing occurs on the surface of the evaporator, and the air passage is narrowed and dried. There is a possibility that the efficiency of heat exchange with the wind is significantly reduced. Therefore, conventionally, control has been performed to temporarily stop the compressor even when the temperature of the evaporator is abnormally lowered.

  Accordingly, there is provided a clothes dryer that is provided with a heat pump and that can prevent a decrease in drying performance while preventing a compressor from being stopped due to occurrence of a temperature abnormality of the refrigerant.

  The clothes dryer of the present embodiment includes a drying chamber in which clothes are stored, a circulation air passage for circulatingly supplying drying air into the drying chamber, a blower that blows drying air in the circulation air passage, and a compressor A heat pump for dehumidifying and heating the drying air, a refrigerant temperature sensor for detecting the temperature of the refrigerant in the heat pump, a drying operation by controlling the blower and the heat pump And a control device that increases the drive frequency of the compressor to a target frequency when the compressor is started up based on the detected temperature of the refrigerant temperature sensor. Is variably controlled.

1 is a vertical right side view schematically showing an internal configuration of a washing / drying machine according to the first embodiment. Rear view schematically showing the internal structure including the heat pump of the washing and drying machine Block diagram showing the electrical configuration of the washing and drying machine A diagram showing the relationship between the evaporator temperature and the amount of change in compressor drive frequency The figure which shows the mode of the change of the evaporator temperature with the passage of time and the change of the compressor drive frequency when the drive frequency at the time of starting of the compressor is a constant rising speed in the energy saving course The figure which shows the mode of the change of the evaporator temperature with the passage of time and the change of the compressor drive frequency when the drive frequency at the time of starting of the compressor is variably controlled in the energy saving course The figure which shows 2nd Embodiment and shows the relationship between condenser temperature and the variation | change_quantity of a compressor drive frequency. The figure which shows 3rd Embodiment and shows the relationship between evaporator temperature and the variation | change_quantity of fan rotation speed. The figure which shows the mode of the fluctuation | variation of the rotation speed of a fan with the passage of time at the time of carrying out variable control of the rotation speed of a fan, and the fluctuation | variation of a compressor drive frequency in an energy saving course. The figure which shows 4th Embodiment and shows the relationship between condenser temperature and the variation | change_quantity of fan rotation speed.

  Hereinafter, some embodiments applied to a drum-type washing and drying machine as a clothes dryer will be described with reference to the drawings. In addition, about the part which is common among several embodiment, such as the hardware constitutions of the washing-drying machine 1, the same code | symbol is attached | subjected and new illustration and description of repetition will be abbreviate | omitted.

(1) First and Second Embodiments A first embodiment will be described with reference to FIGS. First, an overall configuration of a drum-type washing / drying machine 1 as a clothes dryer according to the present embodiment will be described with reference to FIGS. 1 to 3. The outer box 2 constituting the main body of the washing / drying machine 1 has a substantially rectangular box shape, and a cylindrical water tank 3 is inclined downwardly in the outer box 2 through an elastic support mechanism (not shown). It is supported. A cylindrical rotating drum 4 as a rotating tub for storing clothes (laundry) is rotatably supported in the water tub 3. The rotary drum 4 is configured to rotate around an inclined axis that extends in the front-rear direction and is inclined rearwardly downward.

  As shown in FIG. 1, a large number of holes 4 a for water passage and ventilation are formed in the peripheral wall portion and the rear wall portion of the rotating drum 4, and the laundry agitator is formed on the inner surface of the peripheral wall portion of the rotating drum 4. A plurality of baffles (not shown) are provided. Although not shown, the front surface of the rotary drum 4 is provided with an opening through which clothes are put in and out. The front surface of the water tank 3 is formed with a charging port that is continuous with the opening, and the front surface of the outer box 2 is provided with a door 5 that opens and closes the charging port. An operation panel 6 (see FIG. 3) is provided on the upper portion of the front surface of the outer box 2.

  As shown in FIGS. 1 and 2, a drum motor 8 made of, for example, an outer rotor type brushless motor is disposed at the rear of the water tank 3. The tip of the rotating shaft of the drum motor 8 penetrates the back surface of the water tank 3 and protrudes into the water tank 3, and is connected and fixed to the center of the rear part of the rotating drum 4. With such a configuration, the rotary drum 4 is directly driven to rotate by the drum motor 8. The drum motor 8 is provided with a rotation sensor 42 (shown only in FIG. 3) for detecting the rotation of the rotor of the drum motor 8. The rotation sensor 42 functions as a load detection unit that detects the amount of cloth in the rotary drum 4.

  Although not shown in detail, a water supply device for supplying water into the water tank 3 is provided at an upper portion in the outer box 2. This water supply apparatus includes a water supply valve 11 (see FIG. 3) connected to a water tap as a water supply source via a connection hose, a water injection case having a detergent charging case that can be pulled out, and the like. On the other hand, as shown in FIG. 1, a drainage pipe 12 is connected to the lower part of the water tank 3, and a drainage valve 13 is provided in the middle of the drainage pipe 12. When water is supplied from the water supply device into the water tank 3 with the drain valve 13 closed, the water is stored in the water tank 3. At this time, the water level in the water tank 3 is detected by a water level sensor 7 (see FIG. 3). As the drain valve 13 is opened, the water stored in the water tank 3 is discharged to the outside through the drain pipe 12.

  As shown in FIG. 1, the water tank 3 is provided with an air discharge port 17 at a front right side portion of the upper surface and an air supply port 18 at an upper left portion of the back surface portion. As shown in FIGS. 1 and 2, a drying mechanism 19 that circulates and supplies drying air (warm air) into the rotating drum 4 is provided inside the outer box 2. In the present embodiment, the drying mechanism 19 is located outside the water tank 3 and includes a circulation air passage 20 and a heat pump 21. The circulation air passage 20 has an inlet and an outlet, and the inlet is connected to the outlet 17 of the water tank 3 and the outlet is connected to the supply port 18. Further, the drying mechanism 19 includes a blower 22 that supplies air discharged from the discharge port 17 from the supply port 18 into the water tank 3 and thus into the rotating drum 4 while circulating in the circulation air passage 20 in the direction of arrow A. Yes.

  Specifically, the circulation air passage 20 includes an exhaust duct 23, a heat pump duct 24, and an air supply duct 25. Among them, the exhaust duct 23 has a base end connected to the discharge port 17, extends rearward from the upper right side in the outer box 2, and then bends to extend downward from the rear of the water tank 3. 24 is connected to the base end (right end). A well-known lint filter 26 for capturing lint from the dry air is provided at the front end side portion of the exhaust duct 23.

  The heat pump duct 24 extends leftward and rightward at the bottom rear portion in the outer box 2, and the blower 22 is provided on the tip side (right end side in FIG. 2). The blower 22 includes, for example, a centrifugal fan 15 and a fan motor 16 that drives the centrifugal fan 15 in a fan casing 14. A proximal end portion (lower end portion) of the air supply duct 25 is connected to an outlet portion of the fan casing 14. The air supply duct 25 extends rearwardly from the left water tank 3 in the outer box 2, and its tip end (upper end) is connected to the supply port 18.

  As shown in FIG. 2, in the heat pump duct 24, an evaporator 27 and a condenser 28 constituting a heat pump (refrigeration cycle) 21 are sequentially arranged on the right and left (left and right in FIG. 2). The heat pump 21 is configured by connecting a compressor 29, the condenser 28, a throttle valve 30 serving as a pressure reducing device, and the evaporator 27 in a closed loop by a refrigerant pipe 31. As the decompression device, a capillary tube or the like may be employed instead of the throttle valve 30. A required amount of refrigerant is sealed inside the heat pump 21 and circulates through the refrigerant pipe 31. At this time, the condenser 28 functions as a heating unit that heats the drying air, and the evaporator 27 functions as a dehumidifying unit that removes moisture from the drying air.

  In the heat pump 21, the gas refrigerant discharged from the compressor 29 flows into the condenser 28 and is condensed by heat exchange in the condenser 28 when the compressor 29 is driven during the drying operation. Refrigerant. The liquid refrigerant that has flowed out of the condenser 28 is expanded by the throttle valve 30 to form a mist, and the mist refrigerant flows into the evaporator 27. In the evaporator 27, the refrigerant is vaporized by heat exchange with the outside air, and the gaseous refrigerant is returned to the compressor 29. Circulation is performed in which the refrigerant is compressed by the compressor 29 and discharged at a high temperature and high pressure.

  As the heat pump 21 is driven and the blower 22 is driven, the air in the water tank 3 (the rotating drum 4) passes through the exhaust duct 23 from the discharge port 17 as indicated by an arrow A in FIGS. To the heat pump duct 24, flow in the heat pump duct 24, sequentially pass through the evaporator 27 and the condenser 28, then flow into the air supply duct 25, and are supplied into the rotary drum 4 through the supply port 18 and the hole 4a. The cycle is performed. Due to the circulation of the air, the air containing a large amount of steam which is deprived of moisture from the clothes in the water tank 3 (the rotating drum 4) is cooled through the evaporator 27 portion in the heat pump duct 24, so that the steam is The dehumidified air is condensed (or sublimated) and dehumidified, and the dehumidified air is heated by passing through the condenser 28 portion to become dry warm air, which is supplied again into the rotating drum 4 and used for drying clothes. .

  At this time, as shown in FIG. 2, the heat pump 21 is provided with a plurality of temperature sensors that detect the temperature of the refrigerant flowing through the refrigerant flow path 37. Specifically, a compressor outlet temperature sensor 32 is provided on the discharge side of the compressor 29, a condenser temperature sensor 33 is provided on the condenser 28, and an evaporator temperature is provided at the inlet of the evaporator 27. A sensor 34 is provided, and a compressor inlet temperature sensor 35 is provided on the suction side of the compressor 29. Further, as shown in FIG. 1, the air supply duct 25 in the circulation air passage 20 is located near the supply port 18 and detects the temperature of the dry air flowing through the circulation air passage 20. A sensor 36 is provided.

  As shown in FIG. 1, the circulation air passage 20 is opened to the outside in the middle portion of the exhaust duct 23, that is, the upper wall portion of the rear portion of the lint filter 26, that is, the air in the circulation air passage 20 ( An exhaust port 37 is provided as an opening for exhausting the air in the water tank 3 to the outside of the outer box 2. The exhaust port 37 communicates with an outer exhaust port 38 provided in the outer box 2. A damper 39 for opening and closing the exhaust port 37 is provided at the exhaust port 37 portion. The damper 39 is operated using, for example, a damper motor 40 (shown only in FIG. 3) as a drive source.

  As shown in FIG. 2, an intake port 24 a is provided above the heat pump duct 24 so as to be positioned between the evaporator 27 and the condenser 28. The intake port 24a is always open and communicates the inside of the circulation air passage 18 and the outside of the circulation air passage 18. Thus, when the damper 39 is operated in the driving state of the blower 22 and the exhaust port 37 is opened, a part of the air passing through the circulation air passage 20 is exhausted as shown by an arrow B in FIG. The air is exhausted to the outside of the outer box 2 through the port 37 and the outer exhaust port 38. At the same time, as indicated by an arrow C in FIG. 2, outside air is taken into the circulation air passage 18 from the intake port 24a.

  The operation panel 6 is provided with various operation units 10 in addition to a power-on switch, a power-off switch, and a display unit 9 for performing necessary display (all are shown only in FIG. 3). In the present embodiment, the user can operate the operation unit 10 to instruct the execution of the washing and drying operation in which the drying operation is executed continuously after the washing operation. Further, it is possible to select and set an operation course related to the drying operation.

  At this time, in the present embodiment, as a course that can be set for the drying operation, an energy saving course, a rush course, a careful course, and the like are included. Among them, the energy saving course is a course for suppressing power consumption. The driving frequency of the compressor 29 is low, the rotational speed of the blower 22 is low (for example, 3700 rpm), the temperature of the drying air is relatively low, and the drying time is low. Relatively long. The rush course is a course for shortening the drying time. The driving frequency of the compressor 29 is high, the rotation speed of the blower 22 is high (for example, 5000 rpm), the circulating air temperature is high, and the drying time is high. It becomes relatively short. The careful course is a course to dry firmly, the drive frequency of the compressor 29 is high, the rotational speed of the blower 22 is high (5000 rpm), the circulating air temperature is high, and the drying time is long.

  The outer box 2 is provided with a control device 41 as a control means that mainly includes a microcomputer and controls the entire washing and drying machine 1. FIG. 3 schematically shows the electrical configuration of the washing / drying machine 1 of the present embodiment, centering on the control device 41. That is, an operation signal from the operation unit 10 of the operation panel 6 is input to the control device 41, and the control device 41 controls display on the display unit 9 of the operation panel 6.

  The control device 41 receives detection signals from the water level sensor 7, the rotation sensor 42, the temperature sensors 32 to 35 of the heat pump 21, and the drying air temperature sensor 36. Further, the outside air temperature detection signal detected by the outside air temperature sensor 43 is input to the control device 41. The control device 41 controls the water supply valve 11, the drain valve 13, the drum motor 8, the blower 22 (fan motor 16), the compressor 29 and throttle valve 30 of the heat pump 21, and the damper motor 40 (damper 39). At this time, the control device 41 can control the blower 22 (fan motor 16) at a variable rotational speed.

  The compressor 29 employs an inverter motor, and the control device 41 drives the compressor 29 at a variable frequency (rotation speed) by inverter control. In the drying process, the control device 41 controls the drive of the compressor 29 at a target drive frequency (for example, 60 Hz to 80 Hz), but gradually increases to the target frequency when the compressor 29 is started. . At this time, as will be described in detail later, the control device 41 variably controls the rising speed of the drive frequency of the compressor 29.

  With the above-described configuration, the control device 41 can control each mechanism of the washing and drying machine 1 based on an input signal from each sensor or a pre-stored control program in accordance with an operation course set by the user in the operation unit 10. The washing operation including the washing process, the rinsing process, and the dehydrating process, and the above-described drying operation are automatically executed. The washing / drying operation in which the drying operation is performed continuously after the washing operation is also possible. Since each process of the washing operation is well-known and will not be described, at the start of the washing operation, the clothing capacity (cloth amount) is determined based on the load detection on the rotating drum 4, and the determination result is The water level is determined accordingly.

  In the drying operation, the control device 41 drives and controls the blower 22 and the heat pump 21 according to the type of drying course set by the user. Here, when the temperature of the refrigerant in the evaporator 27 becomes too low in the driving state of the heat pump 21, condensation and freezing occur on the surface of the evaporator 27, the air passage is narrowed and the dry air is There is a risk that the heat exchange efficiency will be significantly reduced. A state in which the temperature of the evaporator 27 is abnormally low is referred to as an evaporator low temperature abnormality. In addition, when the heat pump 21 is in a driving state and the internal refrigerant (from the compressor 29 to the condenser 28) reaches a higher temperature and pressure than necessary, the heat pump 21 may be damaged. A state in which the temperature of the refrigerant from the compressor 29 to the condenser 28 becomes abnormally high is referred to as refrigerant high temperature abnormality.

  Therefore, in the present embodiment, as will be described in the following description of the operation, the control device 41 is configured to increase the driving frequency of the compressor 29 to the target frequency when starting up the compressor 29 during the drying process. The temperature detected by the evaporator temperature sensor 34 is monitored, and the rising speed is variably controlled based on the temperature detected by the evaporator temperature sensor 34. More specifically, the speed of increase of the driving frequency of the compressor 29 is variably controlled so that the degree of increase of the driving frequency is increased as the refrigerant temperature detected by the evaporator temperature sensor 34 is higher.

  That is, FIG. 4 shows the relationship between the temperature detected by the evaporator temperature sensor 34 and the drive frequency of the compressor 29 that is raised for one minute, for example. The control device 41 reads the detected temperature of the evaporator temperature sensor 34 every minute. For example, when the detected temperature is less than −10 ° C., the drive frequency of the compressor 29 is decreased by 5 Hz in one minute thereafter. . When the detected temperature is −10 ° C. or higher and lower than 5 ° C., the driving frequency of the compressor 29 is maintained as it is for one minute thereafter. When the detected temperature is 5 ° C. or higher, the driving frequency of the compressor 29 is increased by 5 Hz for 1 minute thereafter.

  Next, the operation of the washing / drying machine 1 having the above configuration will be described with reference to FIGS. Now, for example, when performing a washing / drying operation in which a drying operation is performed continuously after a washing operation, the user puts clothes into the rotating drum 4 and puts a necessary detergent into the detergent charging case, Settings are made by operating the operation unit 10 of the operation panel 6. In this case, the washing / drying operation can be set, and the user's favorite course in the drying process, that is, an energy saving course, a rush course, or a careful course can be selected and set.

  When the washing / drying operation is started, the control device 41 executes a washing operation including a washing process, a rinsing process, and a dehydrating process. At the start of the washing operation, the capacity of the clothes in the rotary drum 4 is determined. When the washing operation is completed, a drying process (drying operation) is subsequently performed. This drying process is executed only for a predetermined drying time (for example, 200 minutes). This drying time is automatically set based on the set course and the capacity of clothing. As described above, in the drying process, the heat pump 21 and the blower 22 are driven, and forward and reverse rotation of the rotating drum 4 at a relatively low speed is repeated at a predetermined cycle.

  As shown by an arrow A in FIG. 2, while the clothes in the rotary drum 4 are loosened by rotation, the dry wind consisting of dry warm air passes through the circulation air passage 20 into the rotary drum 4 (water tank 3). Circulation is supplied and the clothes are dried. As described above, when this drying operation is started, the compressor 29 is started by the control device 41, and is raised from a stopped state (0 Hz) to a target drive frequency (for example, 60 Hz to 80 Hz). Thereafter, the compressor 29 is driven while the target frequency is maintained.

  When the compressor 29 is started, the detected temperature of the evaporator temperature sensor 34 is monitored by the control device 41. As shown in FIG. 4, when the detected temperature of the evaporator temperature sensor 34 is relatively high at 5 ° C. or more based on the detected temperature of the evaporator temperature sensor 34 read every minute, the control device 41 Thereafter, the drive frequency of the compressor 29 is increased by 5 Hz in one minute. On the other hand, when the temperature detected by the evaporator temperature sensor 34 is slightly lower than −10 ° C. and lower than 5 ° C., the current driving frequency of the compressor 29 is maintained for one minute thereafter. When the temperature detected by the evaporator temperature sensor 34 is as low as less than −10 ° C., the drive frequency of the compressor 29 is decreased by 5 Hz in one minute thereafter.

  Thus, when the temperature of the evaporator 27 becomes relatively low at the time of starting the compressor 29, the capacity of the heat pump 21 is maintained or reduced by maintaining or reducing the current driving frequency of the compressor 29. And further temperature drop of the evaporator 27 is prevented. Thereby, the refrigerant | coolant temperature of the evaporator 27 becomes low temperature more than necessary, and the evaporator low temperature abnormality in which freezing generate | occur | produces on the surface of the evaporator 27 is prevented beforehand. When the temperature of the evaporator 27 is relatively high, there is no fear of occurrence of an evaporator low temperature abnormality, and the drive frequency of the compressor 29 is continuously increased by +5 Hz / min to reach the target frequency at an early stage. be able to.

  5 and 6 show the evaporator detected by the evaporator temperature sensor 34 with the passage of time from the start (time T0) to the end (time Te) of the drying process when the drying course is an energy saving course, for example. The state of the fluctuation | variation of the temperature of 27 and the drive frequency of the compressor 29 is illustrated. Among them, FIG. 5 shows the case where the conventional control for increasing the drive frequency at a constant rising speed is performed when the compressor 29 is started, and FIG. 6 shows the case where the control in this embodiment is performed.

  In the example of FIG. 5, since the drive frequency of the compressor 29 is increased to a target frequency (for example, 70 Hz) at a constant increase speed from the start of starting the compressor 29 (time T0) to time Ta, the temperature of the evaporator 27 is increased. The compressor 29 is stopped because an evaporator low temperature abnormality has occurred at time Tb. The compressor 29 is restarted from the time Tc when the temperature of the evaporator 27 is recovered. As described above, when the drive frequency of the compressor 29 is increased to the target frequency at a constant increase speed, the increase in the drive frequency becomes relatively abrupt. It will stop. The blower 22 is driven at a predetermined rotational speed (for example, 4000 rpm) during the drying process.

  On the other hand, in the example of FIG. 6, when the compressor 29 is started, the increase speed of the drive frequency of the compressor 29 is varied according to the temperature of the evaporator 27. That is, from the start of starting the compressor 29 (time T0), for example, the drive frequency of the compressor 29 is increased at +5 Hz / min until the drive frequency reaches 40 Hz (time T1). At time T1, since the temperature detected by the evaporator temperature sensor 34 is in the range of −10 ° C. or higher and lower than 5 ° C., the drive frequency is maintained as it is. At time T2, since the temperature detected by the evaporator temperature sensor 34 is 5 ° C. or higher, the drive frequency of the compressor 29 is increased at +5 Hz / min.

  At time T3, the temperature detected by the evaporator temperature sensor 34 again drops below 5 ° C. (−10 ° C. or higher), so that the driving frequency at that time (for example, 50 Hz) is maintained, and at time T4, the evaporator temperature sensor 34 Since the detected temperature becomes 5 ° C. or higher, the drive frequency of the compressor 29 is increased again at +5 Hz / min. Similar control is repeated, and at time T7, the drive frequency of the compressor 29 reaches the target, and thereafter the target frequency is maintained. As described above, when the temperature of the evaporator 27 becomes relatively low, an increase in the driving frequency of the compressor 29 is suppressed, a decrease in the temperature of the evaporator is suppressed, and an evaporator low temperature abnormality does not occur. In this case as well, the blower 22 is driven at a predetermined rotational speed (for example, 4000 rpm) during the drying process.

  As described above, when the drive frequency of the compressor 29 is increased to the target frequency when the compressor 29 is started up, if the drive frequency of the compressor 29 increases rapidly, the refrigerant temperature in the evaporator 27 is increased. There is a risk that an evaporator low-temperature abnormality in which the temperature drops abnormally. On the other hand, if the speed of increase of the driving frequency of the compressor 29 is made too slow, the ability of the heat pump 21 cannot be fully exhibited, and the drying performance may be reduced. On the other hand, in this embodiment, since the speed of increase of the driving frequency of the compressor 29 is controlled based on the temperature detected by the evaporator temperature sensor 34, an evaporator low temperature abnormality occurs and the compressor 29 is It is possible to control the compressor 29 such that the drying performance can be exhibited as much as possible without being temporarily stopped.

  Therefore, according to the present embodiment, the apparatus provided with the heat pump 21 can control an appropriate driving frequency when the compressor 29 is started, and the compressor 29 is stopped when the refrigerant temperature abnormality occurs. In spite of being able to avoid this, it is possible to prevent the drying performance from being deteriorated. In particular, in the present embodiment, the rate of increase in the drive frequency of the compressor 29 is variably controlled so that the degree of increase in the drive frequency increases as the temperature increases based on the temperature of the evaporator 27 in the heat pump 21. It is possible to appropriately control the rising speed of the drive frequency of the compressor 29 while preventing the occurrence of the low temperature abnormality of the compressor and the temporary stop of the compressor 29 in advance.

  FIG. 7 shows a second embodiment, which differs from the first embodiment in the following points. That is, in the second embodiment, when the compressor 29 is started up, the control device 41 monitors the temperature of the refrigerant in the condenser 28 of the heat pump 21, that is, the detected temperature of the condenser temperature sensor 33. The rising speed of the drive frequency of the compressor 29 is variably controlled so that the degree of increase of the drive frequency of the compressor 29 is increased as the temperature is lower.

  FIG. 7 shows the relationship between the temperature detected by the condenser temperature sensor 33 and the drive frequency of the compressor 29 that is increased per minute. The control device 41 reads the detected temperature of the condenser temperature sensor 33 every minute. For example, when the detected temperature is less than 70 ° C., the drive frequency of the compressor 29 is increased by 5 Hz in one minute thereafter. When the detected temperature is 70 ° C. or higher and lower than 75 ° C., the drive frequency of the compressor 29 is maintained as it is for one minute thereafter. When the detected temperature is 75 ° C. or higher, the drive frequency of the compressor 29 is lowered by 5 Hz for 1 minute thereafter.

  Here, as described above, if the drive frequency rises rapidly when the compressor 29 is started, a refrigerant high temperature abnormality occurs that causes the refrigerant from the compressor 29 to the condenser 28 to reach a higher and higher pressure than necessary. In other words, if a high temperature abnormality of the refrigerant occurs, the compressor 29 may be damaged. On the other hand, in the present embodiment, the rising speed of the drive frequency of the compressor 29 is controlled based on the temperature detected by the condenser temperature sensor 33, so that a refrigerant high temperature abnormality occurs and the compressor 29 is temporarily stopped. It is possible to control the compressor 29 so that the drying performance can be exhibited as much as possible without stopping. Accordingly, it is possible to avoid the stop of the compressor 29 due to the occurrence of the refrigerant temperature abnormality, but it is possible to prevent the drying performance from being deteriorated.

(2) Third and Fourth Embodiments and Other Embodiments FIGS. 8 and 9 show the third embodiment. The difference from the first and second embodiments is the following configuration. It is in. That is, in the first embodiment, the control device 41 controls the drive frequency when the compressor 29 is started. In the present embodiment, instead, the control device 41 after the start of the compressor 29 is controlled. The rotational speed of the blower 22 is variably controlled based on the temperature detected by the refrigerant temperature sensor, in this case, the evaporator temperature sensor 34. The hardware configuration of the washing / drying machine 1 is the same as that of the first and second embodiments.

  At this time, in this embodiment, in the drying process, the control device 41 normally drives the blower 22 at a basic value of, for example, 4000 rpm. And the control apparatus 41 monitors the detection temperature of the evaporator temperature sensor 34 during a drying process, and variably controls the rotation speed of the air blower 22 so that the rotation speed of the air blower 22 may become small, so that detection temperature is high.

  Specifically, as shown in FIG. 8, the control device 41 reads, for example, the detected temperature of the evaporator temperature sensor 34 every minute, and if the detected temperature is lower than −10 ° C., the blower 22 rotates. Increase the number by +200 rpm. When the temperature detected by the evaporator temperature sensor 34 is −10 ° C. or higher and lower than 5 ° C., the rotational speed of the blower 22 is maintained as it is. Or you may make it return to a basic value (4000 rpm). When the temperature detected by the evaporator temperature sensor 34 is relatively high, such as 5 ° C. or higher, the rotational speed of the blower 22 is decreased by 200 rpm. However, the rotational speed control of the blower 22 is performed within the range of the maximum rotational speed (for example, 5800 rpm) and the minimum rotational speed (for example, 1700 rpm).

  Here, when the rotation speed of the blower 22 is increased, the air volume is increased and heat exchange (heat transfer amount) in the heat pump 21 is increased. When the rotation speed of the blower 22 is decreased, the air volume is decreased and the heat transfer amount is increased. Can be reduced. Therefore, when the temperature of the evaporator 27 becomes relatively low, the temperature of the evaporator 27 is further prevented from lowering by increasing the rotational speed of the blower 22. Thereby, the refrigerant | coolant temperature of the evaporator 27 becomes low temperature more than necessary, and the evaporator low temperature abnormality in which freezing generate | occur | produces on the surface of the evaporator 27 is prevented beforehand. When the temperature of the evaporator 27 is relatively high, there is no fear of an evaporator low temperature abnormality, and the energy consumption can be suppressed by reducing the number of rotations of the blower 22.

  FIG. 9 shows the temperature of the evaporator 27 detected by the evaporator temperature sensor 34 with the passage of time from the start (time T0) to the end (time Te) of the drying process when the drying course is an energy saving course, for example. And the mode of the fluctuation | variation of the rotation speed of the air blower 22 is shown. That is, from the start of starting the compressor 29 (time T0), the rotation speed of the blower 22 is increased until reaching the basic value (time T11). When the detected temperature of the evaporator temperature sensor 34 at this time is −10 ° C. or higher and lower than 5 ° C., the rotation speed is maintained. And at time T12, since the temperature detected by the evaporator temperature sensor 34 has become 5 ° C. or higher, the rotational speed of the blower 22 is reduced by 200 rpm.

  Thereafter, for example, at time T13 after 1 minute, the detected temperature of the evaporator temperature sensor 34 is less than 5 ° C. (−10 ° C. or higher), so the rotation speed of the blower 22 is maintained, and then at time T14, the evaporator Since the temperature detected by the temperature sensor 34 is again 5 ° C. or higher, the rotational speed of the blower 22 is further reduced by 200 rpm. At time T15, the rotational speed of the blower 22 is maintained, at time T16, the rotational speed of the blower 22 is again reduced by 200 rpm, and at time T17, the rotational speed of the blower 22 is maintained at that rotational speed.

  By controlling the rotational speed of the blower 22 as described above, the temperature of the evaporator 27 is maintained in a relatively high state, a temperature drop of the evaporator 27 is suppressed, and an evaporator low temperature abnormality does not occur. Note that the drive frequency of the compressor 29 is increased to a target value at a constant rising speed from the start-up, and thereafter maintained at a constant value (target frequency). In this case, the temperature abnormality of the refrigerant can be prevented without performing fine control when the compressor 29 is started.

  According to such 3rd Embodiment, since the rotation speed of the air blower 22 can be controlled based on the detected temperature of a refrigerant | coolant temperature sensor, the temperature abnormality of a refrigerant | coolant can be prevented by the effect | action of the air blower 22. FIG. it can. Therefore, in the apparatus equipped with the heat pump 21, the rotation speed of the blower 22 can be appropriately controlled when the heat pump 21 is driven, and the stop of the compressor 29 due to the occurrence of the refrigerant temperature abnormality can be avoided. However, it is possible to prevent the drying performance from being deteriorated. In particular, in the present embodiment, since the rotational speed of the blower 22 is variably controlled based on the temperature of the evaporator 27 in the heat pump 21, while preventing the occurrence of an evaporator low temperature abnormality and the temporary stop of the compressor 29, The rotation speed of the blower 22 can be appropriately controlled.

  FIG. 10 shows a fourth embodiment, which is different from the third embodiment in the following points. That is, in the present embodiment, the control device 41 monitors the temperature of the refrigerant in the condenser 28 of the heat pump 21, that is, the temperature detected by the condenser temperature sensor 33. Based on the detected temperature, the rotational speed of the blower 22 is variably controlled so that the higher the detected temperature is, the larger the rotational speed is.

  FIG. 10 shows the relationship between the temperature detected by the condenser temperature sensor 33 and the increase / decrease in the rotational speed of the blower 22. For example, the control device 41 reads the detected temperature of the condenser temperature sensor 33 every minute, and when the detected temperature is as low as less than 70 ° C., the control device 41 decreases the rotational speed of the blower 22 by 200 rpm. When the temperature detected by the condenser temperature sensor 33 is 70 ° C. or higher and lower than 75 ° C., the rotational speed of the blower 22 is maintained as it is. When the detected temperature is 75 ° C. or higher, the rotational speed of the blower 22 is increased by +200 rpm. By increasing the rotational speed of the blower 22, heat exchange in the condenser 28 is further promoted, and the temperature of the condenser 28 can be lowered.

  In the fourth embodiment, since the rotation speed of the blower 22 is controlled based on the temperature detected by the condenser temperature sensor 33, the refrigerant flowing from the compressor 29 to the condenser 28 has a higher temperature and pressure higher than necessary. Appropriate control of the blower 22 can be achieved without causing the refrigerant high temperature abnormality to be prevented, causing the refrigerant high temperature abnormality to occur, and temporarily stopping the compressor 29 and exhibiting the drying performance as much as possible. Is possible. Accordingly, it is possible to avoid the stop of the compressor 29 due to the occurrence of the refrigerant temperature abnormality, but it is possible to prevent the drying performance from being deteriorated.

  In each of the above-described embodiments, the temperature detection of the evaporator 27 and the temperature detection of the condenser 28 are described as separate examples as the refrigerant temperature of the heat pump 21, and the driving frequency when the compressor 29 is started up The control of the rotation speed of the blower 22 has been described as separate examples. However, the temperature detection of the evaporator 27 and the temperature detection of the condenser 28 are performed simultaneously, and the control of the drive frequency when the compressor 29 is started, It is also possible to carry out the control in a form in which a plurality of embodiments are combined, such as controlling the rotational speed of the blower 22 at the same time.

  In addition, various modifications can be made to the overall hardware configuration, the type of drying course, and the like, such as being applicable not only to a washing and drying machine but also to a clothes drying machine that does not have a washing function. Furthermore, specific numerical values such as various times, temperatures used as threshold values, the frequency of the compressor 29, and the rotational speed of the blower 22 in each of the above-described embodiments are merely shown as examples. The present invention is not limited to the above-described embodiments, such as being capable of being changed, and various modifications can be made without departing from the spirit of the invention.

  In the drawings, 1 is a washing dryer (clothing dryer), 2 is an outer box, 3 is a water tank, 4 is a rotating drum (drying chamber), 6 is an operation panel, 8 is a drum motor, 16 is a fan motor, and 17 is a drain. Outlet, 18 is a supply port, 19 is a drying mechanism, 20 is a circulation air passage, 21 is a heat pump, 22 is a blower, 24a is an air inlet, 27 is an evaporator, 28 is a condenser, 29 is a compressor, 32 is a compressor An outlet temperature sensor, 33 is a condenser temperature sensor, 34 is an evaporator temperature sensor, 37 is an exhaust port, 38 is an external exhaust port, 39 is a damper, 41 is a control device, 42 is a rotation sensor, and 43 is an outside air temperature sensor. .

Claims (6)

A drying room in which clothing is housed;
A circulation air passage for circulatingly supplying drying air into the drying chamber;
A blower for blowing dry air in the circulation air passage;
A compressor, a condenser, an evaporator, a decompression device, and a heat pump for dehumidifying and heating the dry air;
A refrigerant temperature sensor for detecting the temperature of the refrigerant in the heat pump;
A controller for controlling the blower and the heat pump to perform a drying operation,
The said control apparatus is a clothes dryer which variably controls the rising speed based on the temperature detected by the refrigerant temperature sensor when the driving frequency of the compressor is raised to the target frequency when the compressor is started.   The control device variably controls an increase rate of the compressor driving frequency based on the temperature of the refrigerant in the evaporator of the heat pump so that the degree of increase in the driving frequency increases as the temperature of the refrigerant increases. The clothes dryer according to claim 1.   The control device variably controls the speed of increase of the compressor driving frequency based on the temperature of the refrigerant in the condenser of the heat pump so that the degree of increase in the driving frequency increases as the temperature of the refrigerant decreases. The clothes dryer according to claim 1. A drying room in which clothing is housed;
A circulation air passage for circulatingly supplying drying air into the drying chamber;
A blower for blowing dry air in the circulation air passage;
A compressor, a condenser, an evaporator, a decompression device, and a heat pump for dehumidifying and heating the dry air;
A refrigerant temperature sensor for detecting the temperature of the refrigerant in the heat pump;
A controller for controlling the blower and the heat pump to perform a drying operation,
The said control apparatus is a clothes dryer which variably controls the rotation speed of the said air blower after starting of the said compressor based on the detected temperature of the said refrigerant | coolant temperature sensor.   The clothes according to claim 4, wherein the control device variably controls the rotational speed of the blower based on the temperature of the refrigerant in the evaporator of the heat pump so that the rotational speed is decreased as the temperature of the refrigerant is higher. Dryer.   The clothing according to claim 4, wherein the control device variably controls the rotational speed of the blower based on the temperature of the refrigerant in the condenser of the heat pump so that the rotational speed is increased as the temperature of the refrigerant is higher. Dryer.

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