JP2014045954A - Clothes dryer - Google Patents

Abstract

PROBLEM TO BE SOLVED: To determine whether a start of a refrigeration cycle operation is normal or not at an early stage, and, if it is abnormal, to bring the operation back to normal at an early stage.SOLUTION: A clothes dryer includes: an outer case; a drying chamber; a circulation air path for connecting an exhaust port and an air supply port of the drying chamber; a heat pump unit having a compressor, a decompression device, an evaporator and a condenser; a blower for supplying the air which is dehumidified and heated at the heat pump unit to the drying chamber; a first temperature detection means for detecting air temperature between the condenser and the exhaust port in the circulation air path; a second temperature detection means for detecting air temperature between the evaporator and the exhaust port in the circulation air path; and a control means for controlling the heat pump unit and the blower. The control means determines whether the start of a refrigeration cycle is normal or not during a determination period after the start of the compressor based on the difference of the detection results by the first temperature detection means and the second temperature detection means, and when the start of the refrigeration cycle is determined not to be normal, the compressor is stopped temporarily, and restarted after that.

Description

  Embodiments described herein relate generally to a clothes dryer.

  In recent years, an increasing number of clothes dryers employ a heat pump system as a heating method for warm air for drying clothes. The heat pump type clothes dryer has the advantages that the clothes can be dried at a lower temperature than the heater type, so that the clothes are less damaged by heat, the power consumption is low, and the energy is saved. A heat pump type clothes dryer includes a heat pump unit including an evaporator and a condenser as heat exchangers, a compressor for supplying a refrigerant, and the like. The clothes dryer operates a refrigeration cycle by a heat pump unit, and circulates air between a drying chamber in which clothes are stored and a heat exchanger. As a result, the air containing moisture from the drying chamber is dehumidified and heated by the heat exchanger to become low-humidity warm air, and is supplied to the drying chamber again, thereby drying the clothes in the drying chamber.

  In general, the heat exchanger of such a heat pump unit is composed of a tube having a large number of fins provided at minute intervals, and by flowing a refrigerant through the tube, the heat exchanger unit is connected between the fins of the heat exchanger. Exchanges heat with passing air. When the operation of the refrigeration cycle by the heat pump unit is started, the temperature of the evaporator decreases and the temperature of the condenser increases. In this case, for example, when the ambient temperature is relatively low, such as about 10 ° C. in winter, the evaporator may decrease to a minus temperature in the initial stage of the operation of the refrigeration cycle. At this time, if air with relatively high humidity passes through the evaporator, frost forms on the evaporator, and the frost may increase the air path resistance between the fins.

  If the operation of the refrigeration cycle is continued in this state, the evaporator temperature also rises as the condenser temperature rises, which may eliminate the frosting of the evaporator. Also, frosting on the evaporator side may progress and the fins may be closed. Then, since air does not pass through the evaporator and the condenser, heat exchange is not performed, and the temperature rise of the evaporator and the condenser does not proceed and the operation of the refrigeration cycle does not start up normally.

  If the operation of the refrigeration cycle is started up normally, the temperature of the condenser and the evaporator gradually rises as the drying of the clothes progresses, thereby further drying the clothes. However, when frost forms on the evaporator, the temperature of the condenser and the evaporator does not rise, so that drying of the clothes does not proceed. Therefore, if frost forms on the evaporator at the start of the refrigeration cycle, the period until the frost is eliminated and the operation of the refrigeration cycle returns to normal does not contribute to the drying of clothing, and as a result, Termination is delayed. Therefore, when frost forms on the evaporator, it is necessary to quickly eliminate the frost and return to normal operation.

  In order to eliminate the frost formation of the evaporator, for example, it is conceivable to detect the temperature of the evaporator and control the operation of the compressor according to the temperature. However, frosting does not occur if the passing air is dry even if the evaporator is lowered to a negative temperature. Therefore, when determining whether or not frost formation has occurred due to the temperature of the evaporator, the determination time is when a certain amount of time has elapsed since the start of the operation of the refrigeration cycle, and when it starts normally And after a clear difference in the temperature of the evaporator occurs. For this reason, it was difficult to determine and eliminate at an early stage that frost formation occurred in the evaporator and the refrigeration cycle did not start up normally.

JP 2009-195364 A

  Therefore, a clothes dryer that can determine whether or not the operation of the refrigeration cycle has started normally is early, and if it has not started normally, return to normal operation at an early stage, thereby suppressing the extension of the drying operation. provide.

  The clothes dryer of the present embodiment includes an outer box, a drying chamber provided in the outer box and having an exhaust port and an air supply port, and a circulation provided outside the drying chamber and connecting the exhaust port and the air supply port. An air passage, a compressor, a decompression device, an evaporator provided in the circulation air passage and dehumidifying air in the circulation air passage, and the circulation air passage provided downstream of the evaporator in the circulation air passage. A heat pump unit having a condenser that heats the air therein, a blower that is provided in the circulation air passage and that dehumidifies and heats by the heat pump unit from the air supply port into the drying chamber, and the circulation A first temperature detecting means for detecting an air temperature between the condenser and the air supply port in the air passage; and an air temperature between the evaporator and the exhaust port in the circulation air passage. A second temperature detecting means for detecting, the first temperature And a control unit which controls the heat pump unit and the blower based on a detection result of the degree detecting means and the second temperature detecting means. The control means is based on a difference between detection results obtained by the first temperature detection means and the second temperature detection means within a determination period based on a predetermined period after starting the compressor. It is determined whether or not the rise of the refrigeration cycle is normal, and when it is determined that the rise of the refrigeration cycle is not normal, the compressor is temporarily stopped and then restarted.

1 is a longitudinal side view of the schematic configuration of the clothes dryer according to the first embodiment, partially broken away. Longitudinal rear view showing the schematic configuration of the clothes dryer partially broken Block diagram showing the configuration of the control system The figure which shows schematic structure of the refrigerating cycle by a heat pump unit Graph showing each temperature and the number of rotations of the compressor when the start-up of the refrigeration cycle is normal Graph showing each temperature and the number of rotations of the compressor when the rise of the refrigeration cycle is abnormal Flowchart showing control contents of drying operation by control device The flowchart which shows the control content of the rise determination processing by a control apparatus The flowchart which shows the control content of the abnormality recovery process by a control apparatus Graph showing each temperature and compressor rotation speed when the refrigeration cycle rises abnormally and abnormal recovery processing is executed FIG. 8 equivalent diagram according to the second embodiment FIG. 9 equivalent diagram according to the third embodiment

  Hereinafter, a clothes dryer according to a plurality of embodiments will be described with reference to the drawings. In addition, in each embodiment, the same code | symbol is attached | subjected to the substantially same component, and description is abbreviate | omitted.

(First embodiment)
First, a first embodiment will be described with reference to FIGS.
As shown in FIG. 1, a laundry dryer 10 as a clothes dryer includes an outer box 11, a water tank 12, a rotating tank 13, a motor 14, and a door 15. In the present embodiment, the door 15 side with respect to the outer box 11 is the front side of the washing / drying machine 10. The washing / drying machine 10 is a so-called drum-type washing / drying machine having a heat pump-type drying function, in which the rotation axis of the rotating tub 13 is inclined with respect to the ground. The outer box 11 is formed in a substantially rectangular box shape by a steel plate or the like. The water tank 12 is housed inside the outer box 11. The rotary tank 13 is accommodated in the water tank 12. Both the water tank 12 and the rotating tank 13 are formed in a cylindrical shape.

  The water tank 12 has an opening 121 at one end of a cylindrical shape, and a water tank end plate 122 at the other end. The opening 121 is located above the water tank end plate 122 in the inclined water tank 12. Similarly, the rotating tank 13 has an opening 131 formed at one end of a cylindrical shape, and a rotating tank end plate 132 provided at the other end. The opening 131 is located above the rotating tank end plate 132 in the inclined rotating tank 13. The opening 131 of the rotating tank 13 is covered with the opening 121 of the water tank 12. The water tank 12 and the rotating tank 13 function as a drying chamber for storing clothes.

The water tank 12 has an exhaust port 16 and an air supply port 17. The exhaust port 16 is provided in the upper front portion of the peripheral wall constituting the cylindrical portion of the water tank 12. The air supply port 17 is in the water tank end plate 122 and is provided at a portion slightly above the center of the water tank end plate 122. The exhaust port 16 and the air supply port 17 communicate the inside and the outside of the water tank 12.
Moreover, the water tank 12 has the drainage part 18 in the rear-end side of the bottom part located under the gravity direction. The drainage part 18 is located below the exhaust port 16 and the air supply port 17. The drainage unit 18 includes a drainage port 123, a drainage valve 19, and a drainage hose 20. By opening the drain valve 19, the water in the water tank 12 is discharged from the drain port 123 to the outside of the washing / drying machine 10 via the drain valve 19 and the drain hose 20.

  The rotary tank 13 has a plurality of holes 21 and a plurality of communication ports 22. The hole 21 and the communication port 22 communicate the inside and the outside of the rotary tank 13. The hole 21 is formed in the whole area of the peripheral wall which comprises the cylindrical cylindrical part of the rotating tank 13. As shown in FIG. The communication port 22 is formed in the entire area of the rotary tank end plate 132. The hole 21 and the communication port 22 mainly function as a water passage through which water enters and exits during a washing operation and a dehydration operation, and function as a ventilation hole through which air enters and exits during a drying operation. In FIG. 1, only a part of the plurality of holes 21 and the communication ports 22 is shown for simplicity. Further, although not shown in detail, the rotating tub 13 is provided with a plurality of baffles inside the cylindrical portion. The baffle stirs the laundry stored inside the rotating tub 13.

  The motor 14 is provided on the water tank end plate 122 outside the water tank 12. The motor 14 is, for example, an outer rotor type direct drive motor. The shaft portion 141 of the motor 14 passes through the water tank end plate 122 and protrudes to the inside of the water tank 12, and is fixed to the center portion of the rotary tank end plate 132. Thereby, the motor 14 rotates the rotation tank 13 relatively with respect to the water tank 12. In this case, the shaft portion 141, the rotation axis of the rotating tub 13, and the central axis of the water tub 12 coincide with each other.

  The door 15 is provided on the outer surface side of the outer box 11 via a hinge (not shown). The door 15 rotates about a hinge as a fulcrum, and opens and closes an opening (not shown) formed on the front surface of the outer box 11. The opening formed in the outer box 11 is connected to the opening 121 of the water tank 12 by a bellows 112. Laundry such as clothes is put into and out of the rotating tub 13 through the openings 121 and 131 with the door 15 opened.

  The washing / drying machine 10 includes a control device 23 and an operation panel 24 shown in FIG. 3, and a water supply device 25 shown in FIG. Although not shown in detail, the control device 23 is composed of a microcomputer or the like, and controls the overall operation of the washing / drying machine 10. As shown in FIG. 1, the operation panel 24 is provided in front of the outer box 11 and on the upper side of the door 15. As shown in FIG. 3, the operation panel 24 is connected to the control device 23, and the user performs various settings such as selection of a driving course by operating the operation panel 24.

  As shown in FIG. 2, the water supply device 25 includes a water supply case 26, a water supply valve 27, a water supply hose 28, and the like. The water supply valve 27 is connected to the control device 23 and is opened and closed under the control of the control device 23. One end of the water supply hose 28 is connected to the water supply valve 27 and the other end is connected to an external water source such as a water supply. The control device 23 opens and closes the water supply valve 27 to supply water from the water source into the water tank 12 through the water supply hose 28, the water supply valve 27, and the water supply case 26.

As shown in FIG. 4, the washing / drying machine 10 includes a circulation air passage 30. The circulation air passage 30 connects the exhaust port 16 and the air supply port 17 outside the water tank 12. Specifically, the circulation air passage 30 includes an exhaust duct 31, a filter device 32, a connection duct 33, a heat exchange unit 34, and an air supply duct 35.
As shown in FIG. 1, the exhaust duct 31 connects the exhaust port 16 of the water tank 12 and the filter device 32. The exhaust duct 31 is composed of, for example, a bellows-like hose. The filter device 32 is provided inside the outer box 11 and above the water tank 12 and the rotary tank 13. A filter 321 is provided in the filter device 32. When the air exhausted from the exhaust port 16 passes through the filter 321 of the filter device 32, foreign matters such as lint are removed.

  The filter device 32 is connected to the upstream side of the heat exchanging section 34 via the connection duct 33. The heat exchanging unit 34 is provided in the lower portion inside the outer box 11 and below the filter device 32, the water tank 12, and the rotating tank 13. The heat exchanging unit 34 generates dry hot air by dehumidifying and heating the air passing through the inside. An evaporator 36 and a condenser 37 are provided in the heat exchange unit 34. The evaporator 36 is provided on the upstream side of the condenser 37 with respect to the air flow in the heat exchange unit 34 during the drying operation. The evaporator 36 and the condenser 37 constitute a heat pump unit 40 together with a compressor 38 and a decompression device 39 provided outside the heat exchange unit 34. The air passing through the heat exchange section 34 is cooled by the evaporator 36 and dehumidified thereby. The air dehumidified by the evaporator 36 is then heated by the condenser 37 to become warm air.

  The heat pump unit 40 is configured by sequentially connecting a condenser 37, a decompression device 39, and an evaporator 36 in the refrigerant flow direction with respect to the compressor 38. The evaporator 36 and the condenser 37 are constituted by, for example, a pipe having a large number of fins provided at minute intervals. By flowing the refrigerant through the pipe, heat between the air passing between the fins and the refrigerant is obtained. Exchange. The evaporator 36 and the condenser 37 function as a heat exchanger.

  The compressor 38 supplies the refrigerant to the condenser 37 by pressure feeding. The compressor 38 is connected to the control device 23 and is driven by the control of the control device 23. The compressor 38 is configured such that the drive rotational speed of the compressor 38 can be changed by inverter control, for example. The control device 23 changes the supply pressure of the refrigerant discharged from the compressor 38 by changing the drive rotational speed of the compressor 38, thereby changing the heating capacity of the condenser 37 and the cooling capacity of the evaporator 36. Let The decompression device 39 decompresses the high-pressure liquid refrigerant discharged from the condenser 37 to make a low-pressure gas-liquid mixed state. The decompression device 39 is configured by a so-called electric expansion valve capable of adjusting the throttle opening degree under the control of the control device 23.

  The downstream side of the heat exchange unit 34 is connected to the air supply port 17 of the water tank 12 through the air supply duct 35. A blower 41 is provided at a connection portion between the heat exchange unit 34 and the air supply duct 35. The blower 41 is composed of, for example, a sirocco fan. The blower 41 is configured to be able to change the rotation speed under the control of the control device 23. The blower 41 sucks the air in the heat exchange unit 34 and discharges it to the air supply duct 35 side. Thereby, the flow of the air which circulates through the water tank 12 and the circulation air path 30 arises as shown by the arrow of FIG.1, FIG.2, and FIG.4. In this case, when the air flow in the circulation air passage 30 is viewed, the exhaust port 16 is on the most upstream side, and the air supply port 17 is on the most downstream side.

  In this configuration, when the compressor 38 and the blower 41 are driven for the drying operation, the warm air dehumidified and heated in the heat exchanging section 34 is supplied via the supply duct 35 by the blowing action of the blower 41. It is supplied into the water tank 12 from the air port 17. Thereafter, the warm air mainly enters the rotary tub 13 from the communication port 22, deprives moisture from the laundry in the rotary tub 13, and then mainly exits from the hole 21 to the outside of the rotary tub 13. The air containing moisture is sucked into the circulation air passage 30 from the exhaust port 16. The air sucked into the circulation air passage 30 first passes through the exhaust duct 31 and the filter device 32. At this time, the lint that comes out of the clothes and is contained in the air is collected by the filter 321 provided in the filter device 32. Thereafter, it flows to the heat exchanging section 34 through the connection duct 33. As described above, the drying operation is performed by circulating air between the water tank 12 and the circulation air passage 30 and dehumidifying and heating the air in the circulation air passage 30.

  The washing / drying machine 10 also includes an air inlet temperature sensor 51, an exhaust outlet temperature sensor 52, a compressor discharge side temperature sensor 53, a condenser temperature sensor 54, an evaporator inlet side temperature sensor 55, and an evaporator outlet side temperature sensor. 56. Each temperature sensor 51, 52, 53, 54, 55, 56 is configured by a thermistor, for example, and is connected to the control device 23 as an input device as shown in FIG. 3.

  The air inlet temperature sensor 51 is provided between the condenser 37 and the air inlet 17 in the circulation air passage 30, and the air between the condenser 37 and the air inlet 17 in the circulation air passage 30. Detect the temperature. The air inlet temperature sensor 51 functions as first temperature detection means. In this case, the air supply port temperature sensor 51 is provided in the air supply duct 35 and in the vicinity of the air supply port 17. The air inlet temperature sensor 51 passes through the air supply duct 35 and is supplied to the water tank 12 and the rotary tank 13 that are drying chambers, that is, air that is heated by the heat exchanging section 34 and is supplied to the drying chamber. Detect the temperature. Note that the temperature detected by the air inlet temperature sensor 51 is expressed as an air supply side temperature Ts.

  The exhaust port temperature sensor 52 is provided between the evaporator 36 and the exhaust port 16 in the circulation air passage 30, and the temperature of the air between the evaporator 36 and the exhaust port 16 in the circulation air passage 30. To detect. The exhaust port temperature sensor 52 functions as second temperature detection means. In this case, the exhaust port temperature sensor 52 is provided in the vicinity of the exhaust port 16 in the exhaust duct 31. The exhaust port temperature sensor 52 detects the temperature of the air that is exhausted from the water tank 12 and the rotary tank 13 that are drying chambers and passes through the exhaust duct 31. The temperature detected by the exhaust port temperature sensor 52 is represented as the exhaust side temperature Te.

  The compressor discharge side temperature sensor 53 is provided on the refrigerant discharge side of the compressor 38 and detects the temperature of the refrigerant discharged from the compressor 38. The compressor discharge side temperature sensor 53 functions as a compressor discharge side temperature detection means. The temperature detected by the compressor discharge side temperature sensor 53 is represented as a compressor discharge side temperature Td. The condenser temperature sensor 54 is provided in the condenser 37 and detects the temperature of the condenser 37. The condenser temperature sensor 54 functions as a condenser temperature detection means. The temperature detected by the condenser temperature sensor 54 is represented as the condenser temperature Tc. The evaporator inlet side temperature sensor 55 is provided on the refrigerant inlet side of the evaporator 36 and detects the temperature of the refrigerant flowing into the evaporator 36. The evaporator outlet side temperature sensor 56 is provided on the refrigerant outlet side of the evaporator 36 and detects the temperature of the refrigerant flowing out of the evaporator 36. The temperature detected by the evaporator inlet side temperature sensor 55 is expressed as an evaporator inlet side temperature Ti, and the temperature detected by the evaporator outlet side temperature sensor 56 is expressed as an evaporator outlet side temperature To.

  Next, when the compressor 38 and the blower 41 are started, the temperatures Ts, Te, Td, Tc, Ti, and To when the refrigeration cycle by the heat pump unit 40 starts up normally and when it does not start up normally are set. The change will be described with reference to FIGS. 5 and 6, the outside air temperature is about 10 ° C., and the temperatures Ts, Te, Td, Tc, Ti, and To before starting the compressor 38 are substantially the same as the outside air temperatures. Yes. Further, the state where the refrigeration cycle by the heat pump unit 40 has started means that the air that is dehumidified and heated by the heat exchange unit 34 and supplied from the air supply port 17 to the water tank 12 and the rotary tank 13 is the clothing in the rotary tank 13. Is ready to be dried.

  When the refrigeration cycle starts up normally, as shown in FIG. 5, the compressor discharge side temperature Td and the condenser temperature Tc are approximately the same temperature increase rate for about 20 minutes after starting the compressor 38. It rises by about ℃. Thereafter, the rate of temperature increase of the compressor discharge side temperature Td and the condenser temperature Tc becomes moderate. In this case, after about 20 minutes from the start of the compressor 38, the temperature increase rate of the condenser temperature Tc becomes gentler than the temperature increase rate of the compressor discharge side temperature Td, and the compressor discharge side temperature Td The temperature difference from the condenser temperature Tc gradually increases. Then, the compressor discharge side temperature Td and the condenser temperature Tc rise at a constant rate in a period of about 20 minutes to 140 minutes after the start of the compressor 38, and then the temperature rise slows around 140 minutes. Thereafter, the temperature is maintained at a substantially constant temperature. In this case, the compressor discharge side temperature Td is maintained at about 100 ° C., and the condenser temperature Tc is maintained at about 70 ° C.

  The supply-side temperature Ts and the exhaust-side temperature Te rise as the condenser temperature Tc rises when the compressor 38 is started. At this time, in the period of about 30 minutes after the compressor 38 is started, the temperature increase rate of the supply side temperature Ts is larger than the temperature increase rate of the exhaust side temperature Te. For this reason, in the period of about 30 minutes after the compressor 38 is started, the temperature difference between the supply side temperature Ts and the exhaust side temperature Te is 0.5 ° C. or more per minute. Increase by 1 ° C. Thereafter, after about 30 minutes from the start of the compressor 38, the temperature increase of the supply side temperature Ts becomes moderate, and the temperature increase rates of the supply side temperature Ts and the exhaust side temperature Te become substantially the same. . For this reason, the supply side temperature Ts and the exhaust side temperature Te rise while maintaining a constant temperature difference, for example, a temperature difference of about 20 ° C., for a period of about 30 minutes to 140 minutes. At this time, the air that has passed through the heat exchanging section 34 and has become dry hot air takes moisture from the clothes in the rotating tub 13 and exchanges heat, thereby causing the clothes to dry.

  Then, about 140 after the start of the compressor 38, the temperature rise of the condenser temperature Tc slows down and is maintained at a substantially constant temperature, and the temperature rise of the supply side temperature Ts also slows down to a substantially constant temperature. In that case maintained at about 50 ° C. Thereafter, after about 180 minutes, the drying of the garment is almost finished, and as a result, the temperature rise of the exhaust side temperature Te becomes moderate, and the temperature difference between the supply side temperature Ts and the exhaust side temperature Te is reduced. Then, when the temperature difference between the supply side temperature Ts and the exhaust side temperature Te becomes equal to or less than a predetermined value, for example, 15 ° C., it is determined that the drying of the clothes has ended and the drying operation is ended.

  The evaporator inlet side temperature Ti and the evaporator outlet side temperature To maintained the temperature difference between the evaporator inlet side temperature Ti and the evaporator outlet side temperature To during a period of about 10 minutes after the compressor 38 was started. It decreases rapidly. Thereafter, when no frost is formed in the evaporator 36, or when frost is formed but the frost is quickly eliminated by the heat of the condenser 37, the evaporator 36 evaporates as the condenser temperature Tc rises. The evaporator inlet side temperature Ti and the evaporator outlet side temperature To also rise. And with the slowing of the temperature rise of the condenser temperature Tc after about 180 minutes, the temperature rise of the evaporator inlet side temperature Ti and the evaporator outlet side temperature To is also slowed and maintained at a substantially constant temperature. In this case, the evaporator inlet side temperature Ti is maintained at about 20 ° C., and the evaporator outlet side temperature To is maintained at about 18 ° C.

  The period from the start to the end of the drying operation by the heat pump unit 40 is roughly divided into an initial R1, an intermediate R2, and a late R3, focusing on the progress of clothing drying. The initial R1 indicates the rising period of the refrigeration cycle by the heat pump unit 40. In this initial R1, the air that passes through the heat exchanging section 34 and is supplied from the air supply port 17 into the water tank 12 and the rotary tank 13 hardly contributes to drying of the clothes. The middle period R2 indicates a period that greatly contributes to the progress of drying of the clothes. During the middle period R2, the air that has passed through the heat exchanging section 34 and is supplied from the air supply port 17 into the water tank 12 and the rotary tank 13 deprives the clothes of moisture and exchanges heat with the clothes, thereby drying the clothes. To advance. The latter period R3 indicates a period in which most of the drying of the clothes is finished and the progress of the drying is slowed down. After the latter period R3, the drying operation is terminated.

  In this embodiment, when the refrigeration cycle starts up normally as shown in FIG. 5, the initial R1 is about 30 minutes after the refrigeration cycle is started, that is, a period from 0 minutes to 30 minutes. The middle period R2 is about 150 minutes after the initial period R1, that is, a period from 30 minutes to 180 minutes. The latter period R3 is a period after the lapse of the middle period R2, that is, a period after 180 minutes.

  On the other hand, when the refrigeration cycle does not start up normally, as shown in FIG. 6, the evaporator inlet side temperature Ti and the evaporator outlet side temperature To are about 10 minutes after the compressor 38 is started. It is declining rapidly. At this time, since the evaporator inlet side temperature Ti has decreased to a minus temperature, frost starts to adhere to the evaporator 36 when the ambient humidity is high. Then, about 20 minutes after the start of the compressor 38, the evaporator 36 is closed by frost formed on the evaporator 36. In this case, after the compressor 38 is started, the compressor discharge side temperature Td and the condenser temperature Tc rise during a period until the evaporator 36 is blocked by frost formation. However, if the amount of air circulating in the circulation air passage 30 decreases due to the blockage of the evaporator 36, heat exchange between the evaporator 36 and the condenser 37 and the air in the circulation air passage 30 is not performed. Then, the heat of the condenser 37 is not transmitted to the evaporator 36, and the temperature rise of the condenser 37 and the evaporator 36 becomes moderate. As a result, the temperature rise of the compressor discharge side temperature Td and the condenser temperature Tc is also gentle. become.

  Further, after the compressor 38 is started, the period until the evaporator 36 is blocked by frosting, that is, the period up to about 20 minutes, is the supply side temperature Ts and the exhaust side temperature as the condenser temperature Tc rises. Te also rises. However, after about 20 minutes, as the condenser temperature Tc rises gradually, the rises in the supply side temperature Ts and the exhaust side temperature Te also moderate. In this case, the temperature difference between the supply side temperature Ts and the exhaust side temperature Te is approximately 0. 0 minutes per minute, as in the case where the rise of the refrigeration cycle is normal in a period of about 20 minutes after the compressor 38 is started. In the case of the present embodiment at 5 ° C. or higher, the temperature increases by about 1 ° C. per minute. However, after about 20 minutes have passed since the compressor 38 was started, the temperature difference between the supply side temperature Ts and the exhaust side temperature Te hardly changes to about 0.2 ° C. per minute.

  Thereafter, the frost generated in the evaporator 36 is gradually eliminated over time as the condenser 37 gradually rises in temperature. When the blockage of the evaporator 36 due to frosting begins to be eliminated, the flow rate of the air flowing through the circulation air passage 30 gradually increases. Then, since the heat exchange between the cold air passing through the evaporator 36 and the condenser 37 is performed, as shown in a period of about 180 minutes to 200 minutes in FIG. 6, the condenser temperature Tc, the supply side temperature Ts, and the compressor The discharge side temperature Td temporarily decreases. Thereafter, as shown in a period of about 200 minutes to 220 minutes, the elimination of frost formation of the evaporator 36 is promoted, and the condenser temperature Tc, the supply side temperature Ts, and the compressor discharge side temperature Td are increased. The evaporator inlet side temperature Ti and the evaporator outlet side temperature To also rise.

  Then, after about 220 minutes, the supply side temperature Ts and the exhaust side temperature Te are increased as the compressor discharge side temperature Td and the condenser temperature Tc increase as in the period after about 30 minutes shown in FIG. The temperature rises while maintaining a constant temperature difference, for example, a temperature difference of around 20 ° C. At this time, the air that has passed through the heat exchanging section 34 and has become low-humidity warm air takes moisture from the clothes in the rotating tub 13 and exchanges heat, thereby causing the clothes to dry. Thereafter, the drying operation is terminated through the latter period R3. In this case, after about 220 minutes in FIG. 6, the process proceeds in substantially the same manner as after about 30 minutes in FIG.

  Thus, when the refrigeration cycle does not start up normally, the initial R1, which is the rising period of the refrigeration cycle, is about 220 minutes after the start of the refrigeration cycle as shown in FIG. Although not shown in detail, the middle period R2 is a period of about 150 minutes after the initial R1, that is, about 220 minutes to 370 minutes, as in the case where the refrigeration cycle shown in FIG. The latter period R3 is a period after the lapse of the middle period R2, that is, a period after about 380 minutes. In this case, the rising period R1 when the refrigeration cycle starts up normally, that is, the initial R1 is about 30 minutes as shown in FIG. 5, whereas the rising period R1 when the refrigeration cycle does not start up normally is shown in FIG. About 220 minutes. That is, the time required for the drying operation requires an extra difference of the rising period R1, that is, 190 minutes when the refrigeration cycle does not start up normally compared to when it normally starts up.

  As described above, when the rise of the refrigeration cycle becomes abnormal, the temperature rise of the condenser 37 is moderate during the period until the abnormality is resolved and the normal state is restored. do not do. For this reason, when frost forms on the evaporator 36 and the rise of the refrigeration cycle becomes abnormal, it is desirable to eliminate the frost on the evaporator 36 as soon as possible. However, it is difficult to detect frost formation on the evaporator 36 at an early stage by monitoring the temperature of the evaporator 36. This is because the temperature of the evaporator 36, that is, the evaporator inlet side temperature Ti and the evaporator outlet side temperature To change slowly during the rising period R1 of the refrigeration cycle, as shown in FIGS. For example, the evaporator inlet side temperature Ti and the evaporator outlet side temperature To at a normal rise shown in FIG. 5 and the evaporator inlet side temperature Ti and the evaporator outlet side temperature To at an abnormal rise shown in FIG. The difference occurs only after about 30 minutes have elapsed since the start of the refrigeration cycle.

  Thus, when determining whether or not the refrigeration cycle has started up normally based on the temperature of the evaporator 36, the determination is based on the temperature of the evaporator 36 when the refrigeration cycle has started up normally and the refrigeration cycle is normal. It is necessary to make a difference after a clear difference is found between the temperature of the evaporator 36 when it is not raised. That is, in this case, whether or not the refrigeration cycle has started up normally is determined by a period during which the temperature of the evaporator 36 is expected to be sufficiently increased if the refrigeration cycle has started up normally, in other words, It is necessary to wait for a while after the rising period R1 when the refrigeration cycle has started up normally. For this reason, when it is determined whether or not the refrigeration cycle has started up normally based on the temperature of the evaporator 36, the determination cannot be made at an early stage, and therefore the frost formation of the evaporator 36 can be eliminated at an early stage. It was difficult.

  Therefore, in the present embodiment, the control device 23 is based on the difference between the supply side temperature Ts that is the detection result of the supply port temperature sensor 51 and the exhaust side temperature Te that is the detection result of the exhaust port temperature sensor 52. It is determined whether the rising of the refrigeration cycle by the heat pump unit 40 is normal. The determination is made within a determination period P based on the passage of a predetermined period after the compressor 38 is started. In the case of the present embodiment, the determination period P is set to 10 minutes from the start of the compressor 38 until 30 minutes after the lapse of 20 minutes. This is because, in this determination period P, the difference between the supply side temperature Ts and the exhaust side temperature Te between the case where the refrigeration cycle starts up normally and the case where it does not start up normally appears relatively large. For example, in this embodiment, the change in the difference between the supply side temperature Ts and the exhaust side temperature Te in a period of about 20 minutes to 30 minutes, which is a relatively early period after the start of the compressor 38, indicates that the refrigeration cycle starts up normally. In this case, as shown in FIG. 5, the temperature is about 0.5 ° C. or more per minute, in this case, about 1 ° C. per minute. On the other hand, when the refrigeration cycle does not start up normally, the temperature is about 0.2 ° C. per minute as shown in FIG.

  As shown in FIG. 7, when the drying operation is started, the control device 23 sets the throttle opening K = k1 of the decompression device 39 in step S11, and starts the compressor 38 at the rotational speed H = h1 in step S12. In step S13, the blower 41 is started at the rotation speed F = f1. Thereby, the refrigerating cycle by the heat pump unit 40 is started. Note that the refrigerant flowing through the decompression device 39 increases in flow rate and decreases in pressure drop as the throttle opening K increases. Further, the pressure of the refrigerant pumped by the compressor 38 increases as the rotational speed H increases. And the ventilation volume by the air blower 41 increases, so that the rotation speed F is large.

  When the control device 23 starts the refrigeration cycle through steps S11, S12, and S13, the control device 23 executes a rising determination process in step S14. In the rising determination process, the control device 23 determines that the rising of the refrigeration cycle is normal if the amount of change in the difference between the supply side temperature Ts and the exhaust side temperature Te in the determination period P is greater than or equal to the threshold, and is less than the threshold. If so, it is determined that the rising of the refrigeration cycle is abnormal.

  Specifically, as shown in FIG. 8, when executing the rising determination process, the control device 23 determines whether or not 20 minutes have elapsed since the start of the refrigeration cycle in step S21, that is, whether or not the start of the determination period P has been reached. Judging. If 20 minutes have not elapsed since startup (NO in step S21), step S21 is repeated until 20 minutes have elapsed after startup. Thereafter, when 20 minutes have elapsed since the start of the refrigeration cycle (YES in step S21), the control device 23 proceeds to step S22, and the supply side temperature Ts1 at the start of the determination period P, that is, 20 minutes after the start of the refrigeration cycle. And the exhaust side temperature Te1 is detected.

  Thereafter, the control device 23 proceeds to step S23 and determines whether 30 minutes have elapsed since the start of the refrigeration cycle, that is, whether or not the end of the determination period P has been reached. If 30 minutes have not elapsed since startup (NO in step S23), step S23 is repeated until 30 minutes have elapsed since startup. Thereafter, when 30 minutes have elapsed since the start of the refrigeration cycle (YES in step S23), the control device 23 proceeds to step S24, and the supply side temperature Ts2 at the end of the determination period P, that is, 30 minutes after the start of the refrigeration cycle. And the exhaust side temperature Te2 is detected.

Thereafter, in step S25, the control device 23 determines the temperature difference between the supply side temperature Ts1 and the exhaust side temperature Te1 at the beginning of the determination period P, and the temperature of the supply side temperature Ts2 and the exhaust side temperature Te1 at the end of the determination period P. Based on the rate of change with the difference, it is determined whether the refrigeration cycle has started up normally. In this case, when the temperature difference between the supply side temperature Ts and the exhaust side temperature Te changes by 5 ° C. or more before and after the determination period P of 10 minutes, the control device 23 satisfies the following expression (1) ( YES in step S25), the process proceeds to step S27 and it is determined that the rising of the refrigeration cycle is normal.
(Ts2-Te2)-(Ts1-Te1) ≧ 5 ° C. (1)

  On the other hand, when the change in the temperature difference between the supply side temperature Ts and the exhaust side temperature Te is less than 5 ° C. before and after the determination period (NO in step S25), the control device 23 proceeds to step S26 and proceeds to the refrigeration cycle. Is determined to be abnormal. In this case, it can be determined that frost formation has occurred in the evaporator 36. Thereafter, the control device 23 proceeds to step S15 shown in FIG.

  If the rise of the refrigeration cycle is normal in step S15 (YES in step S15), the control device 23 proceeds to step S17. On the other hand, when the rise of the refrigeration cycle becomes abnormal due to frost formation of the evaporator 36 (NO in step S15), the process proceeds to step S16 to execute abnormality recovery processing. When executing the abnormality recovery process, the control device 23 temporarily stops the compressor 38 in step S31 shown in FIG. Then, the pressure of the refrigerant on the condenser 37 side decreases, and it flows into the evaporator 36 side at a relatively high temperature without being vaporized by the evaporator 36. As a result, the temperatures of the condenser 37 and the evaporator 36 are balanced, and the temperature of the entire refrigeration cycle is made uniform. That is, as shown in a period of about 30 minutes to 40 minutes in FIG. 10, the temperature of the condenser 37 decreases and the temperature of the evaporator 36 increases, and as a result, the frosting of the evaporator 36 is eliminated.

Then, in step 42, the control device 23 determines whether or not a sufficient time, for example, 1 minute has passed since the compressor 38 was temporarily stopped to eliminate frosting of the evaporator 36. If one minute has not elapsed (NO in step S32), step S32 is repeated until one minute has elapsed. Thereafter, when one minute has elapsed from the temporary stop of the compressor 38 (YES in step S32), the control device 23 proceeds to step S33 and restarts the compressor 38 at the rotation speed H = h1. Then, as shown in a period of about 40 minutes to 50 minutes in FIG. 10, the compressor discharge side temperature Td, the condenser temperature Tc, and the supply side temperature Ts rise. As a result, the elimination of frost formation in the evaporator 36 is promoted, and as a result, the rising abnormality of the refrigeration cycle is recovered. When the refrigeration cycle is restarted and the rising abnormality is recovered, the drying operation is performed from about 50 minutes to about 200 minutes in FIG. It becomes the middle term R2 indicated by the period of minutes. In the middle period R2, the air supply side temperature Ts and the exhaust side temperature Te gradually rise to advance the drying of the clothes. Thereafter, the drying operation reaches late R3. When the refrigeration cycle is restarted, the control device 23 proceeds to step S17 shown in FIG. In step S17, the control device 23 detects the supply side temperature Ts and the exhaust side temperature Te. In step S18, the end of the drying operation is determined based on the difference between the supply side temperature Ts and the exhaust side temperature Te.

  For example, the control device 23 ends the drying operation on the condition that the difference between the supply side temperature Ts and the exhaust side temperature Te is 15 ° C. or less. That is, if the difference between the supply side temperature Ts and the exhaust side temperature Te is greater than 15 ° C. (NO in step S18), the control device 23 repeats step S17 and step S18 and continues the drying operation. Thereafter, when the difference between the supply-side temperature Ts and the exhaust-side temperature Te is 15 ° C. or less (YES in step S18), it is determined that the clothes are sufficiently dried, the compressor 38 is stopped, and the drying operation is terminated. . Although not shown in detail, a cooling operation may be performed in which the clothes are cooled by blowing air from the blower 41 after the drying operation is completed.

  In this case, as shown in FIG. 10, the rising period R1 is about 50 minutes after the start of the refrigeration cycle. Further, the middle period R2 is from 50 minutes to 150 minutes of 200 minutes after the start of the refrigeration cycle. The latter period R3 is after the middle period R2, that is, after 200 minutes. Thus, even when the rise of the refrigeration cycle becomes abnormal, the compressor 38 is temporarily stopped and the abnormality recovery process is performed, thereby suppressing the rise period R1 of the refrigeration cycle to about 50 minutes. it can. This is only about 20 minutes longer than the rising period R1 = 30 minutes when the refrigeration cycle starts up normally. In other words, the extension period R1 of about 20 minutes when the abnormality recovery process is performed is only about one-tenth of the extension period 190 minutes of the startup period R1 when the abnormality recovery process is not performed. .

  According to this, the control device 23 determines whether or not the start-up of the refrigeration cycle by the heat pump unit 40 is normal within 20 to 30 minutes after the start of the compressor 38 which is the initial stage of the drying operation. A period P is set. In this determination period P, the control device 23 determines the difference between the supply side temperature Ts that is the detection result of the supply port temperature sensor 51 and the exhaust side temperature Te that is the detection result of the exhaust port temperature sensor 52. Based on this, it is determined whether or not the rising of the refrigeration cycle by the heat pump unit 40 is normal. When the controller 23 determines that the rise of the refrigeration cycle is not normal, the controller 38 temporarily stops the frosting of the evaporator 36 to recover the rise of the refrigeration cycle.

  As a result, the control device 23 determines whether or not the operation of the refrigeration cycle by the heat pump unit 40 has started normally at an early stage between 20 minutes and 30 minutes after the start of the compressor 38, which is the initial stage of the drying operation. Can do. If the refrigeration cycle has not started up normally, it can be returned to normal operation at an early stage. As a result, even if the refrigeration cycle does not start up normally due to frosting of the evaporator 36, the drying operation can be performed. Significant extension can be suppressed.

  Whether or not the refrigeration cycle has started up normally is determined based on a change in the difference between the supply side temperature Ts by the supply port temperature sensor 51 and the exhaust side temperature Te by the exhaust port temperature sensor 52. According to this, the change in the difference between the supply side temperature Ts and the exhaust side temperature Te is clarified relatively early after the start of the compressor 38 when the refrigeration cycle starts up normally and when it does not start up normally. There is a big difference. Therefore, it can be determined relatively early after the start of the compressor 38 whether or not the refrigeration cycle has started up normally. As a result, even when frost formation occurs in the evaporator 36 and the rise of the refrigeration cycle becomes abnormal, the frost formation can be eliminated relatively early and the normal operation can be recovered. Extension of drying operation due to abnormality can be suppressed.

(Second embodiment)
Next, a second embodiment will be described with reference to FIG.
In the second embodiment, the control device 23 adds the difference between the supply side temperature Ts by the supply port temperature sensor 51 and the exhaust side temperature Te by the exhaust port temperature sensor 52 to the compressor by the compressor discharge side temperature sensor 53. Based on the discharge side temperature Td, it is determined whether or not the rising of the refrigeration cycle by the heat pump unit 40 is normal. In this case, the content of the rising determination process is different from that of the first embodiment. In the rising determination process shown in FIG. 11, the control device 23 executes step S41 instead of step S22 in the rising determination process of the first embodiment shown in FIG. 8, and executes step S42 instead of step S24. Further, step S43 is executed after step S25.

Specifically, in step S41, the control device 23 detects the compressor discharge side temperature Td1 in addition to the detection of the supply side temperature Ts1 and the exhaust side temperature Te1. In step S42, the compressor discharge side temperature Td2 is detected in addition to the supply side temperature Ts2 and the exhaust side temperature Te2. If the temperature difference between the supply side temperature Ts and the exhaust side temperature Te has changed by a threshold value, for example, 5 ° C. or more before and after the determination period P (YES in step S25), the control device 23 proceeds to step S43. . In step S43, it is further determined whether or not the rising of the refrigeration cycle is normal based on the change in the compressor discharge side temperature Td in the determination period P. The threshold value of the rising temperature of the compressor discharge side temperature Td in the determination of the rise of the refrigeration cycle is set to 3 ° C., for example. If the rising temperature of the compressor discharge side temperature Td is 5 ° C. or higher in the determination period P of 10 minutes in step S43, the control device 23 satisfies the following expression (2) (YES in step S43). ), The process proceeds to step S27, and it is determined that the rising of the refrigeration cycle is normal.
Td2−Td1 ≧ 5 ° C. (2)
On the other hand, when the rising temperature of the compressor discharge side temperature Td is less than 5 ° C. before and after the determination period (NO in step S43), the control device 23 proceeds to step S26 and the rise of the refrigeration cycle is abnormal. to decide.

  According to this, the control device 23 determines whether or not the refrigeration cycle by the heat pump unit 40 has started normally based on the difference between the supply side temperature Ts and the exhaust side temperature Te and the compressor discharge side temperature Td. Do it twice. Therefore, it is possible to more accurately determine whether or not the refrigeration cycle has started up normally. Thereby, it is reduced that the compressor is stopped and the rise of the refrigeration cycle is affected even though the refrigeration cycle is normally started, and as a result, unnecessary extension of the drying operation can be suppressed.

  In the second embodiment, the control device 23 performs the condensation by the condenser temperature sensor 54 in addition to the difference between the supply side temperature Ts by the supply port temperature sensor 51 and the exhaust side temperature Te by the exhaust port temperature sensor 52. Based on the vessel temperature Tc, it may be determined whether or not the rise of the refrigeration cycle by the heat pump unit 40 is normal. In this case, the control device 23 detects the condenser temperature Tc1 instead of the compressor discharge side temperature Td1 in step S41. In step S42, the condenser temperature Tc2 is detected instead of the compressor discharge side temperature Td2. And in step S43, if the rise temperature of the condenser temperature Tc in the determination period of 10 minutes is more than a predetermined threshold value (it is YES at step S43), the control apparatus 23 will transfer to step S27, and the rising of a refrigerating cycle will be carried out. Judge that it is normal. Also by this, the same effect as the above can be obtained.

(Third embodiment)
Next, a third embodiment will be described with reference to FIG.
In the third embodiment, the contents of the abnormality recovery process are different from the above embodiments. Specifically, when starting the abnormality recovery process, the controller 23 first temporarily stops the compressor 38 in step S31 as shown in FIG. In step S51, the throttle opening K of the decompression device 39 is changed to k = k2. The throttle opening k2 is set larger than the throttle opening k1 of the decompression device 39 before the compressor 38 is temporarily stopped. In this case, the throttle opening k2 may be fully opened. In step S32, the control device 23 determines whether, for example, one minute has elapsed since the compressor 38 was temporarily stopped. If one minute has not elapsed (NO in step S32), step S32 is repeated until one minute has elapsed. When one minute has elapsed from the temporary stop of the compressor 38 (YES in step S32), the control device 23 proceeds to step S52.

  The control device 23 changes the throttle opening K of the pressure reducing device 39 to k = k3 in step S52, and changes the rotation speed F of the blower 41 to f2 in step S53. In this case, the throttle opening k3 is set to be larger than the throttle opening k1 before the compressor 38 is temporarily stopped and to be equal to or smaller than the throttle opening k2 when the compressor 38 is temporarily stopped. The rotation speed f2 is set to a value larger than the rotation speed f1 before the compressor 38 is temporarily stopped.

  Thereafter, in step S54, the control device 23 restarts the compressor 38 at the rotation speed H = h2. In this case, the rotation speed h2 is set to a value smaller than the rotation speed h1 before the compressor 38 is temporarily stopped. After restarting the compressor 38, the control device 23 determines in step S55 whether or not a predetermined period, for example, 10 minutes has elapsed since the compressor 38 was restarted. If 10 minutes have not elapsed (NO in step S55), step S55 is repeated until 10 minutes have elapsed. Thereafter, when 10 minutes have elapsed since the restart of the compressor 38 (YES in step S55), the control device 23 changes the throttle opening K of the decompression device 39 to k = k1 in step S56, and the rotational speed of the blower 41 in step S57. F is changed to f1, and the rotational speed H of the compressor 38 is changed to h1 in step S58. Thereby, the throttle opening K of the decompression device 39, the rotational speed F of the blower 41, and the rotational speed H of the compressor 38 are returned to the settings before the compressor 38 is temporarily stopped. Thereafter, the control device 23 proceeds to step S17 shown in FIG. 7 (return), whereby the rising abnormality of the refrigeration cycle is recovered.

  As described above, when the control device 23 temporarily stops the compressor 38, the control device 23 increases the throttle opening K of the decompression device 39 to a throttle opening k2 larger than the throttle opening k1 before the compressor 38 is temporarily stopped. Let According to this, when the compressor 38 is temporarily stopped, the high-temperature high-pressure refrigerant on the condenser 37 side easily flows to the evaporator 36 side on the low-pressure side. Thereby, the pressure and temperature balance between the high pressure side of the refrigeration cycle, that is, the condenser 37 side, and the low pressure side, that is, the evaporator 36 side, is achieved at an early stage. Therefore, the temperature of the evaporator 36 can be increased at an early stage. As a result, the frost attached to the evaporator 36 can be removed at a relatively early stage after the compressor 38 is temporarily stopped. As a result, even if the refrigeration cycle rises abnormally, normal operation can be quickly restored.

  Further, when restarting the compressor 38, the control device 23 reduces the rotational speed H of the compressor 38 to a rotational speed h2 smaller than the rotational speed h1 before the compressor 38 is temporarily stopped. According to this, when the compressor 38 is restarted, the pressure of the refrigerant discharged from the compressor 38 becomes lower than before the temporary stop, and the temperature drop of the evaporator 36 is suppressed. Therefore, it is possible to reduce the occurrence of frost formation again in the evaporator 36 due to the restart of the compressor 38, and thus it is possible to avoid the occurrence of the refrigeration cycle rising abnormality again after the restart of the compressor 38.

  Further, when restarting the compressor 38, the control device 23 increases the rotational speed F of the blower 41 to a rotational speed f2 that is larger than the rotational speed f1 before the compressor 38 is temporarily stopped. According to this, since the amount of air circulating through the circulation air passage 30 increases, heat exchange between the condenser 37 and the evaporator 36 is promoted, so that the temperature of the evaporator 36 is kept relatively high. Therefore, even if frosting occurs again in the evaporator 36 after the compressor 38 is restarted, the progress of the frosting is suppressed. Therefore, it is possible to avoid the occurrence of frost formation again in the evaporator 36 due to the restart of the compressor 38 and the evaporator 36 being blocked, and thus, after the compressor 38 is restarted, the refrigeration cycle is restarted. It is possible to avoid a rise abnormality.

  When the control device 23 restarts the compressor 38, the control device 23 increases the throttle opening K of the decompression device 39 to a throttle opening k3 larger than the throttle opening k1 before the compressor 38 is temporarily stopped. According to this, when the compressor 38 is restarted, the high-temperature refrigerant on the condenser 37 side flows to the evaporator 36 side in a relatively high temperature state. Thereby, since the temperature of the evaporator 36 easily rises, when the compressor 38 is restarted, the temperature drop of the evaporator 36 can be suppressed. Therefore, it is possible to reduce the occurrence of frost formation again in the evaporator 36 due to the restart of the compressor 38, and thus it is possible to avoid the occurrence of the refrigeration cycle rising abnormality again after the restart of the compressor 38.

In the first embodiment and the second embodiment, the decompression device 39 may not be able to change the throttle opening K.
Further, when the compressor 38 is temporarily stopped in the abnormality recovery process, the rotational speed may be decreased without completely stopping the compressor 38.
In each of the above embodiments, the first temperature detection means is the air supply port temperature sensor 51 provided in the vicinity of the air supply port 17, and the second temperature detection means is the exhaust port temperature sensor 52 provided in the vicinity of the exhaust port 16. It was. However, the present invention is not limited to this, and the first temperature detection means is a temperature sensor provided in the vicinity of the condenser 37 in the circulation air passage 30, and the second temperature detection means is in the vicinity of the evaporator 36 in the circulation air passage 30. It may be a provided temperature sensor.
Moreover, although each said embodiment was set as the drum type washing-drying machine which had the washing-drying function, it is not restricted to this, For example, the clothes dryer which does not have a washing function may be sufficient.

  According to the configuration of the embodiment described above, the clothes dryer includes the first temperature detecting means for detecting the temperature of the air between the condenser and the air supply port in the circulation air passage, and the evaporation in the circulation air passage. Second temperature detecting means for detecting the temperature of the air between the vessel and the exhaust port. The control means starts up the refrigeration cycle by the heat pump unit based on a difference between detection results of the first temperature detection means and the second temperature detection means within a determination period based on a predetermined period after starting the compressor. It is determined whether or not is normal. When it is determined that the rise of the refrigeration cycle is not normal, the compressor is temporarily stopped and then restarted.

  According to this, it is determined whether or not the refrigeration cycle has started up normally based on the difference between the detection results of the first temperature detection means and the second temperature detection means. The difference in detection results between the first temperature detection means and the second temperature detection means differs between when the refrigeration cycle starts up normally and when it does not start relatively early after the compressor is started. Therefore, the determination period for determining whether or not the refrigeration cycle has started up normally can be set relatively early after the compressor is started. As a result, even if an abnormality occurs in the rise of the refrigeration cycle, it is possible to return to normal operation at an early stage, and as a result, it is possible to suppress a significant extension of the drying operation due to an abnormal rise of the refrigeration cycle. .

  Although several embodiments of the present invention have been described, these embodiments are presented by way of example and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and equivalents thereof.

  In the drawing, 10 is a washing dryer (clothing dryer), 11 is an outer box, 12 is a water tank (drying chamber), 13 is a rotating tank (drying chamber), 16 is an exhaust port, 17 is an air supply port, and 23 is a control. Device (control means), 30 is a circulation air passage, 36 is an evaporator, 37 is a condenser, 38 is a compressor, 39 is a decompression device, 40 is a heat pump unit, 41 is a blower, 51 is an inlet temperature sensor (first (One temperature detection means), 52 is an exhaust port temperature sensor (second temperature detection means), 53 is a compressor discharge side temperature sensor (compressor discharge side temperature detection means), and 54 is a condenser temperature sensor (condenser temperature detection means). ).

Claims (8)

An outer box,
A drying chamber provided in the outer box and having an exhaust port and an air supply port;
A circulation air passage provided outside the drying chamber and connecting the exhaust port and the air supply port;
A compressor, a pressure reducing device, an evaporator provided in the circulation air passage for dehumidifying the air in the circulation air passage, and an air in the circulation air passage provided downstream of the evaporator in the circulation air passage. A heat pump unit having a condenser for heating;
A blower that supplies air dehumidified and heated by the heat pump unit provided in the circulation air passage from the air supply port to the drying chamber;
First temperature detecting means for detecting the temperature of air between the condenser and the air supply port in the circulation air passage;
Second temperature detection means for detecting the temperature of air between the evaporator and the exhaust port in the circulation air passage;
Control means for controlling the heat pump unit and the blower based on detection results of the first temperature detection means and the second temperature detection means,
The control means is based on a difference between detection results obtained by the first temperature detection means and the second temperature detection means within a determination period based on a predetermined period after starting the compressor. A clothes dryer that determines whether or not the rise of the refrigeration cycle is normal and determines that the rise of the refrigeration cycle is not normal and then pauses and restarts the compressor. The first temperature detection means is provided in the circulation air passage and in the vicinity of the air supply port,
The clothes dryer according to claim 1, wherein the second temperature detecting means is provided in the circulation air passage and in the vicinity of the exhaust port. A compressor discharge side temperature detecting means for detecting the temperature of the refrigerant on the discharge side of the compressor;
The control means has a normal rising of the refrigeration cycle based on a detection result by the compressor discharge side temperature detection means in addition to a difference between detection results by the first temperature detection means and the second temperature detection means. The clothes dryer according to claim 1 or 2, wherein it is determined whether or not. A condenser temperature detecting means for detecting the temperature of the condenser;
The control means determines whether the rising of the refrigeration cycle is normal based on the detection result by the condenser temperature detection means in addition to the difference between the detection results by the first temperature detection means and the second temperature detection means. The clothes dryer of Claim 1 or 2 which judges whether. The decompression device is capable of adjusting the throttle opening by the control of the control means,
The clothes dryer according to any one of claims 1 to 4, wherein when the compressor is temporarily stopped, the control means increases the throttle opening of the pressure reducing device more than before the temporary stop.   The clothes dryer according to any one of claims 1 to 5, wherein when the compressor is restarted, the control means reduces the number of rotations of the compressor from before the temporary stop.   The clothes dryer according to any one of claims 1 to 6, wherein when the compressor is restarted, the control means increases the rotational speed of the blower more than before the temporary stop. The decompression device is capable of adjusting the throttle opening by the control of the control means,
The clothes dryer according to any one of claims 1 to 7, wherein when the compressor is restarted, the control means increases the throttle opening degree of the pressure reducing device more than before the temporary stop.

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