JP2015156943A - clothes dryer - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress excessive temperature rise of a compressor motor without interrupting a drying operation.SOLUTION: A clothes dryer includes: a drying chamber provided in a circulation air passage; a blower for circulating air in the circulation air passage; a heat pump in which a coil for a motor for a compressor is configured by an aluminum wire, which includes a refrigeration cycle configured by connecting a compressor, a condenser, throttle means, and an evaporator by a refrigerant pipe into a closed loop, and which comprises by providing the evaporator in the circulation air passage and providing the condenser in the circulation air passage further on the downstream side with respect to the air flow than the evaporator; a discharge refrigerant temperature sensor for detecting temperature of the refrigerant discharged from the compressor; and control means for performing control so that when the detection temperature by the discharge refrigerant temperature sensor becomes equal to or greater than a preset predetermined temperature, operation capacity of the compressor is reduced and blowing air capacity of the blower is increased.

Description

  Embodiments described herein relate generally to a clothes dryer.

  2. Description of the Related Art A clothes dryer, for example, a household laundry dryer, is provided with a drying operation using a heat pump instead of a drying operation using a conventional heater. In addition to the heat pump, the washer / dryer includes a circulation air passage that is connected to the air supply port and the exhaust port of the water tank and a blower that circulates the air in the water tank through the circulation air path. The heat pump includes a refrigeration cycle. In the refrigeration cycle, a compressor, a condenser, a throttle means, and an evaporator are connected in order to a closed loop through a refrigerant pipe, and the refrigerant is compressed by the compressor, depressurized by the throttle means, and condensed (heat radiation) by the condenser. Evaporation (cooling) is performed in a circulating manner.

  The evaporator is disposed in the circulation air passage on the exhaust port side of the water tank, and the condenser is disposed on the air supply port side of the evaporator. Therefore, air discharged from the exhaust port of the water tank by the operation of the blower is once dehumidified by being cooled by the evaporator, and then heated by the condenser (heated) to supply air to the water tank. It is supplied into the water tank through the mouth, and the clothes in the water tank are deprived of moisture and exit from the exhaust port.

Drying using this heat pump has advantages such as excellent energy efficiency, lower heating temperature, and less wrinkles and shrinkage compared to drying using a heater.
On the other hand, if the temperature of the refrigerant discharged from the compressor rises excessively, the cooling action of the refrigeration cycle will be extremely reduced and the refrigeration cycle will not operate normally, so the refrigerant discharge temperature in the compressor is set at a preset upper limit. When the temperature is reached, the operation of the heat pump including the refrigeration cycle is stopped (heat pump abnormal stop function).

JP 2012-139087 A JP 2003-184775 A

In the washing / drying machine equipped with the heat pump described above, various reviews have been made from the viewpoint of cost reduction. As one of them, it is known to employ a compressor in which a winding of a compressor motor is composed of an aluminum wire which is not a copper wire but has a low material cost.
However, when an aluminum wire is used as the winding of the compressor motor, the electrical resistance is larger and the amount of heat generated is larger than that of the copper wire, and the compressor temperature rises excessively. When the temperature of the compressor rises excessively, the temperature of the discharged refrigerant rises to the abnormality determination temperature, and the heat pump abnormality stop function frequently works. The drying operation is interrupted each time. In this case, since a certain amount of natural heat dissipation time is required before the heat pump can be started up after stopping, it takes a long time to restart the heat pump.

  Therefore, in a clothes dryer equipped with a compressor that uses an aluminum wire for the winding of the compressor motor, an excessive temperature rise of the compressor motor can be suppressed without interrupting the drying operation, and the drying time due to the interruption of the drying operation The clothes dryer which can prevent the extension of the as much as possible.

  The clothes dryer of the embodiment communicates the outer box, a drying chamber provided in the outer box and having an exhaust port and an air supply port, and the exhaust port and the air supply port provided outside the drying chamber. A compressor, a condenser, and a throttle comprising a circulation air passage, a blower provided in the circulation air passage and circulating the air in the drying chamber and the circulation air passage, and a compressor motor winding made of aluminum wire And a refrigeration cycle in which the evaporator is connected in a closed loop with a refrigerant pipe, the evaporator is provided in the circulation air passage, and the condenser is flowed into the circulation air passage from the evaporator. The heat pump provided on the downstream side, the discharge refrigerant temperature sensor for detecting the temperature of the refrigerant discharged from the compressor, and the temperature detected by the discharge refrigerant temperature sensor are equal to or higher than a preset predetermined temperature. Sometimes the luck of the compressor And a control means for controlling to increase the blowing capacity of the blower as well as reduce the capacity.

Longitudinal side view of the washing and drying machine according to the first embodiment Compressor side view Diagram showing schematic configuration of heat pump Functional block diagram of control system Flow chart showing control contents of control device The flowchart which shows the control content of the control (A) according to temperature The flowchart which shows the control content of control (B) according to temperature The flowchart which shows the control content of control (C) according to temperature The figure which shows each adjustment value of a compressor and an air blower The figure which shows schematic structure of the heat pump by 2nd Embodiment. Functional block diagram of control system Flow chart showing control contents of control device The flowchart which shows the control content of the control (A) according to temperature The flowchart which shows the control content of control (B) according to temperature The flowchart which shows the control content of control (C) according to temperature The figure which shows the control form of each adjustment value of a compressor and an air blower, and an automatic expansion valve The figure which shows schematic structure of the heat pump by 3rd Embodiment. Functional block diagram of control system Flow chart showing control contents of control device The flowchart which shows the control content of the control (A) according to temperature The flowchart which shows the control content of control (B) according to temperature The flowchart which shows the control content of control (C) according to temperature The figure which shows each control value of a compressor and an air blower, and the control form of the air blower for compressors

  In the first embodiment, a laundry dryer is shown as a clothes dryer. This washing / drying machine will be described with reference to FIGS. In FIG. 1, a water tank 2 is disposed inside the outer box 1, and a drum 3 is disposed inside the water tank 2. Both the water tank 2 and the drum 3 have a cylindrical shape with one end closed. In this case, the water tank 2 and the drum 3 constitute a tank used for washing clothes (detergent washing and rinsing), dehydration and drying. The interior of the water tank 2 (substantially the interior of the drum 3) constitutes a drying chamber 3a.

  The water tank 2 and the drum 3 have respective openings 4 and 5 on the front side, that is, on the left end surface in FIG. Among these, the opening 5 of the drum 3 is where clothes are put in and out, and the opening 5 is surrounded by the opening 4 of the water tank 2. The opening 4 is connected via a bellows 7 to an opening 6 for putting in and taking out clothes formed on the front surface of the outer box 1. A door 8 is provided at the opening 6 of the outer box 1 so as to be openable and closable.

  The drum 3 is provided with, for example, a liquid-filled rotary balancer 9 around the opening 5, and a hole 10 is formed in the circumferential side, that is, almost the entire region of the drum 3 (one in FIG. 1). Only the part is shown). The hole 10 functions as a water passage hole during washing and dehydration, and functions as a ventilation hole during drying. A plurality of baffles 11 are provided on the inner surface of the peripheral side portion of the drum 3 so as to protrude inward of the drum 3. A plurality of hot air inlets 12 are formed in the end surface portion on the rear side of the drum 3 by an annular arrangement concentric with the center thereof.

  The water tank 2 has an exhaust port 13 formed in the upper part of the front end surface, that is, in a portion above the opening 4, and is opposed to the rotation trajectory of the hot air inlet 12 in the upper part of the rear end surface part. An air supply port 14 is formed. A drain port 15 is provided at the bottom of the water tank 2. A drain valve 16 is connected to the drain port 15 outside the water tank 2, and further, a drain hose 17 is connected to the drain valve 16 so that the water in the water tank 2 can be discharged out of the machine.

  A washing machine motor 18 is attached to the back surface of the water tub 2, and the rotation shaft 19 is inserted into the water tub 2, and the center portion of the rear end surface portion of the drum 3 is attached to the front end portion thereof. ing. Thereby, the drum 3 is coaxially supported by the water tank 2 so that rotation is possible. That is, the drum 3 is directly rotated by the washing machine motor 18, and a direct drive system using the washing machine motor 18 is employed.

  The water tank 2 is elastically supported by the outer box 1 via a plurality of suspensions 20 (only one is shown in FIG. 1). As for the support form, the axial direction of the water tank 2 has a horizontal axis shape that is front and rear and an upwardly inclined shape. Further, the drum 3 supported by the water tank 2 has the same form. In this case, the washing machine motor 18 is constituted by an outer rotor type brushless DC motor, and functions as a driving means for rotating the drum 3.

  A base plate 21 is disposed below the water tank 2, that is, on the bottom surface of the outer box 1, and a ventilation duct 22 is disposed on the base plate 21. The ventilation duct 22 has an air inlet 23 at the top of the front end. An exhaust port 13 of the water tank 2 is connected to the air suction port 23 via a return air duct 24 and a connection hose 25. The return air duct 24 is piped so as to bypass the right side (the right side when viewed from the rear) of the opening 4 of the water tank 2.

  A casing 27 of the blower 26 is connected to the rear end portion of the ventilation duct 22. The outlet portion 28 of the casing 27 is connected to the air supply port 14 of the water tank 2 via a connection hose 29 and an air supply duct 30. The air supply duct 30 is piped so as to bypass the left side of the washing machine motor 18. Here, the exhaust port 13 and the air supply port 14 of the water tank 2 are connected in communication by the return air duct 24, the connection hose 25, the air flow duct 22, the casing 27 of the blower 26, the connection hose 29, and the air supply duct 30, A circulation air passage 31 is configured. The circulation air passage 31 communicates with the water tank 2 and also with the drum 3. In this case, the blower 26 is a centrifugal fan, and has a centrifugal impeller 32 inside the casing 27 and a blower motor 33 that rotates the centrifugal impeller 32 outside the casing 27. The blower 26 constitutes a blower that circulates the air in the drum 3 through the circulation air passage 31. By operating the blower 26, a circulating air flow indicated by an arrow E is formed in the circulating air passage 31. The blower motor 33 can change the rotation speed.

  An evaporator 34 is disposed in the circulation duct 31 on the exhaust outlet 13 side, which is the air outlet side of the drying chamber 3a, inside the ventilation duct 22. Further, a condenser 35 is disposed in the circulation air passage 31 in the ventilation duct 22 on the downstream side of the circulation air flow (air flow) from the evaporator 34. Although neither of these evaporator 34 and condenser 35 are shown in detail, they are tube-shaped with fins in which a large number of heat transfer fins are arranged at a fine pitch on the refrigerant flow pipe, and are excellent in heat exchange. Thus, the circulating air flow (circulating wind) in the ventilation duct 22 passes between the heat transfer fins.

  As shown in FIG. 3, the evaporator 34 and the condenser 35 constitute a heat pump 37 that is a hot air supply means together with a compressor 36 and a capillary tube 43 that is a throttling means. The refrigeration cycle 49 is configured by connecting the machine 36, the condenser 35, the capillary tube 43, and the evaporator 34, which is a dehumidifying means, in a closed loop by the refrigerant pipe 37a.

  The refrigerant is circulated when the compressor 36 is operated. As shown in FIG. 2, the compressor 36 includes, for example, a rotary compression mechanism 36b in a compressor casing 36a, and a compressor motor 36c that drives the compression mechanism 36b. The compressor motor 36c has a rotor 36d and a stator 36e, and the winding 36f of the stator 36e is made of an aluminum wire. The compressor 36 sucks refrigerant (gas refrigerant) from the suction port 36g, compresses it by the compression mechanism 36b, and discharges it from the discharge port 36h.

  The compressor motor 36c of the compressor 36 is inverter-controlled (control of operating frequency) based on a control command from a control device described later, and is controlled to operate at a variable frequency. By increasing the operating frequency, the rotational speed of the compressor 36 is increased.

  The capacity (drying capacity) of the heat pump 37 is determined by the operation frequency (operation capacity) of the compressor 36 and the rotation speed of the blower 26 (rotation speed of the blower motor 33, blower capacity). That is, the higher the operating frequency of the compressor 36, the higher the operating capacity of the compressor 36, and the higher the rotational speed of the blower 26, the higher the blowing capacity of the blower 26, that is, the greater the amount of blown air.

  As shown in FIG. 1, a power supply system control unit 38 and a display system control unit 39 necessary for controlling the washing / drying machine and water supply for supplying water into the aquarium 2 are provided in the inner upper portion of the outer box 1. A valve 40, a water supply case 41, and a water supply hose 42 are disposed. An exhaust temperature sensor 44 for detecting the exhaust temperature is provided in the vicinity of the exhaust port 13 inside the circulation air passage 31, and the supply air temperature for detecting the supply air temperature in the vicinity of the supply port 14. A sensor 45 is provided. Further, as shown in FIG. 3, the evaporator 34 is provided with an evaporator inlet refrigerant temperature sensor 46 for detecting the inlet refrigerant temperature of the evaporator 34 and an evaporator outlet refrigerant temperature sensor 47 for detecting the outlet refrigerant temperature. It has been.

A discharge refrigerant temperature sensor 48 that detects the temperature of the refrigerant discharged from the compressor 36 is provided at the discharge port 36 h of the compressor 36.
FIG. 4 shows a functional block diagram of the control system. The control device 50 includes the control units 38 and 39 (see FIG. 1), and is composed of, for example, a microcomputer, RAM, ROM, or the like. The control device 50 functions as a control unit by executing a control program stored in advance.

  Various operation signals are input to the control device 50 from an operation unit 51 which is an operation unit for a user to perform an operation related to the operation of the washing and drying machine. Then, various displays including the operation result, the current driving situation, and an abnormality display are displayed on the display unit 52 as display means including a liquid crystal display, for example. Further, a water level detection signal is input to the control device 50 from a water level sensor 53 provided to detect the water level in the water tank 2. The controller 50 receives temperature detection signals from the various temperature sensors 44 to 48.

  The control device 50 includes a water supply valve 40 provided to supply water into the water tank 2 (inside the drum 3), and a washing machine motor for driving the drum 3 based on various input signals and a control program stored in advance. 18. Drive control of control targets such as a drain valve 16 provided to drain water from the water tank 2 (inside the drum 3), a compressor motor 36c of the compressor 36, and a blower motor 33 of the blower 26 via a drive circuit 54. To do. The drive circuit 54 includes various drive circuits corresponding to each control target.

The control contents of the control device 50 will be described with reference to the flowcharts of FIGS.
The drying process (drying operation) performed based on control of the control apparatus 50 is demonstrated. The drying process may be performed after the washing process (this includes a detergent washing process, a rinsing process, and a dehydrating process) or may be performed independently.

  It is assumed that the dehydrated clothing is accommodated in the drum 3 before the drying process is performed. In the drying process, as shown in FIG. 5, the control device 50 performs initial setting in step S10. In this initial setting, the operating frequency of the compressor 36 is set to a predetermined initial value, for example, 60 Hz, and the rotational speed of the blower 26 is set to a predetermined initial value, for example, 4000 rpm.

In step S20, the drum 3 is rotated in both forward and reverse directions at a low speed by rotating the washing machine motor 18 in a forward and reverse direction at a low speed.
In the next step S30, the compressor motor 36c of the compressor 36 is operated at the currently set operating frequency, in this case 60 Hz, and the fan motor 33 of the blower 26 is driven at the currently set speed, in this case 4000 rpm. (The fan 26 is operated). Due to the operation of the blower 26, a circulating air flow is generated by the air blowing action of the centrifugal impeller 32 as shown by a solid arrow E in FIG. That is, the air in the water tank 2 flows into the ventilation duct 22 from the exhaust port 13 through the return air duct 24 and the connection hose 25. At this time, by the operation of the compressor 36 of the heat pump 37, the refrigerant sealed in the heat pump 37 is compressed to become a high-temperature and high-pressure refrigerant, and the high-temperature and high-pressure refrigerant flows into the condenser 35, Exchange heat with air. As a result, the air in the ventilation duct 22 is heated, and conversely, the temperature of the refrigerant is lowered and liquefied. The liquefied refrigerant then passes through the capillary tube 43 and is decompressed, and then flows into the evaporator 34 and evaporates. Thereby, the evaporator 34 cools the air in the ventilation duct 22. The refrigerant that has passed through the evaporator 34 returns to the compressor 36.

  As a result, the air flowing into the ventilation duct 22 from the water tank 2 is cooled by the evaporator 34 and dehumidified, and then heated by the condenser 35 to be warmed. Then, the hot air is supplied into the water tank 2 from the air supply port 14 through the connection hose 29 and the air supply duct 30, and is further supplied into the drum 3 from the hot air introduction port 12. The hot air supplied into the drum 3 takes away moisture from the clothes, and then flows into the ventilation duct 22 from the exhaust port 13 through the return air duct 24 and the connection hose 25. As described above, air circulates between the ventilation duct 22 having the evaporator 34 and the condenser 35 and the drum 3, that is, the circulation air passage 31, thereby drying the clothes in the drum 3.

  Note that when the compressor motor 36c is operated, the winding 36f made of an aluminum wire generates heat. Since this heat generation is transmitted to the refrigerant in the compressor 36, the temperature of the refrigerant rises due to heat generated by the compression and heat generated by the winding 36f. In this case, since the winding 36f is made of an aluminum wire, the temperature rise degree is slightly large.

  When a predetermined time interval, for example, 0.5 minute interval has elapsed from the start of the drying process (determined in step S40), a discharge refrigerant temperature tc [° C.] that is a temperature detected by the discharge refrigerant temperature sensor 48 is acquired (step S50). A temperature change rate Δtc [° C./min] is calculated (step S60).

If it is determined that the discharged refrigerant temperature tc is a predetermined temperature, for example, 80 ° C. or more (determined in step S70), control (A) corresponding to the temperature is executed (step S80).
This control content is shown in the flowchart of FIG. 6 as a subroutine. In FIG. 6, if the temperature change rate Δtc is +2 [° C./min] or more (determined in step Q10), the operating frequency of the compressor 36 (compressor motor 36c) is lowered by 10 Hz and the rotational speed of the blower 26 is decreased. Increase by 500 rpm (step Q20). Lowering the operating frequency of the compressor 36 (compressor motor 36c) (lowering the operating capacity) suppresses the rise in the temperature of the refrigerant compressed and discharged by the compressor 36 and also suppresses the amount of power supplied to the winding 36f. Thus, the temperature rise of the winding 36f is also suppressed. Further, by increasing the rotational speed of the blower 26 (increasing the blowing capacity), the circulating air volume per unit time in the circulating air passage 31 increases. As a result, the refrigerant temperature in the condenser 35 decreases and the refrigerant temperature in the evaporator 34 increases, so that the load as the refrigeration cycle, that is, the load on the compressor motor 36c decreases. Therefore, the control for increasing the rotational speed of the blower 26 can also contribute to a decrease in the temperature of the winding 36f.

  If “NO” in the step Q10, the process shifts to a step Q30. If it is determined in this step Q30 that the temperature change rate Δtc is not less than 0 [° C./min] and less than +2 [° C./min], the operating frequency of the compressor 36 is lowered by, for example, 5 Hz and the rotational speed of the blower 26 is reduced. For example, it is increased by 250 rpm (step Q40). In this case as well, the temperature of the winding 36f can be lowered as described above.

If “NO” in the step Q30, the process shifts to a step Q50. In step Q50, neither the operating frequency of the compressor 36 nor the rotational speed of the blower 26 is changed.
Returning to FIG. 5, if “NO” in the step S70, the process shifts to a step S90. In this step S90, it is determined whether or not the discharged refrigerant temperature tc is 60 ° C. or higher and lower than 80 ° C., and if it is 60 ° C. or higher and lower than 80 ° C., control (B) corresponding to the temperature is executed (B). Step S100). This control content is shown in the flowchart of FIG. 7 as a subroutine. In FIG. 7, if the temperature change rate Δtc is equal to or higher than +2 [° C./min] (determined in step R10), the rotational frequency of the blower 26 is increased by 250 rpm without changing the operating frequency of the compressor 36 (step R20). ). Increasing the rotational speed of the blower 26 increases the amount of circulating air in the circulating air passage 31 per unit time, which can contribute to a decrease in the temperature of the winding 36f as described above.

  If “NO” in the step R10, the process shifts to a step R30. If it is determined in step R30 that the temperature change rate Δtc is not less than 0 [° C./min] and less than +2 [° C./min], neither the operation frequency of the compressor 36 nor the rotational speed of the blower 26 is changed (step S30). Q40). If “NO” in the step R30, the process proceeds to a step R50. In step R50, the operating frequency of the compressor 36 is increased by 2 Hz, for example, and the rotational speed of the blower 26 is decreased by 50 rpm, for example.

  If “NO” in the step S90 in FIG. 5, the process proceeds to a step S110. In this step S110, it is determined whether or not the discharged refrigerant temperature tc is 40 ° C. or more and less than 60 ° C., and if it is 40 ° C. or more and less than 60 ° C., control (C) corresponding to the temperature is executed (C). Step S120). This control content is shown in the flowchart of FIG. 8 as a subroutine. In FIG. 8, if the temperature change rate Δtc is +2 [° C./min] or more (determined in step T10), the rotational frequency of the blower 26 is increased by, for example, 150 rpm without changing the operating frequency of the compressor 36 (step S10). T20). Increasing the rotational speed of the blower 26 increases the amount of circulating air in the circulating air passage 31 per unit time, which can contribute to a decrease in the temperature of the winding 36f as described above.

If “NO” in the step T10, the process shifts to a step T30. If it is determined in step T30 that the temperature change rate Δtc is not less than 0 [° C./min] and less than +2 [° C./min], neither the operation frequency of the compressor 36 nor the rotational speed of the blower 26 is changed (step S30). T40). If “NO” in the step T30, the process shifts to a step T50. In step T50, the operating frequency of the compressor 36 is increased by, for example, 6 Hz, and the rotational speed of the blower 26 is decreased by, for example, 200 rpm.
If “NO” in the step S110 of FIG. 5, the process proceeds to a step S130. In step S130, neither the operating frequency of the compressor 36 nor the rotational speed of the blower 26 is changed.

In addition, each adjustment value of the compressor 36 and the air blower 26 in the above-mentioned control is shown in FIG.
In the above embodiment, as can be understood from the control of “YES” in step S70 and step S80 (step Q10, step Q20), the control device 50 detects the temperature detected by the discharged refrigerant temperature sensor 48 at a predetermined temperature set in advance. For example, when the temperature becomes 80 ° C. or higher, the operation capacity of the compressor 36 is reduced (the operation frequency is lowered by 10 Hz) and the air blowing capacity of the blower 26 is increased (increased by 500 rpm).

  That is, first, it is determined whether or not the temperature detected by the discharged refrigerant temperature sensor 48 (discharged refrigerant temperature tc) is a predetermined temperature set in advance, for example, 80 ° C. or higher, so that the compressor motor 36c excessively increases in temperature. It can be judged that Then, when the discharge refrigerant temperature reaches a preset predetermined temperature, for example, 80 ° C. or higher, the heat generation of the winding 36f of the compressor motor 36c can be reduced by reducing the operating capacity of the compressor 36. Further, by increasing the blowing capacity of the blower 26, the load of the refrigeration cycle itself and hence the load of the compressor motor 36c can be reduced, and the heat generation of the winding 36f of the compressor motor 36c can be reduced. Thus, an excessive temperature rise of the compressor motor 36c can be suppressed without stopping the compressor 36 and the blower 26, that is, without stopping the drying operation, and as a result, a temperature drop of the compressor motor 36c can also be expected. Therefore, an excessive temperature rise of the compressor motor 36c can be suppressed without interrupting the drying operation, and extension of the drying time due to the interruption of the drying operation can be prevented as much as possible.

Moreover, by controlling the compressor 36 and the blower 26 at the same time, the temperature rise of the compressor motor 36c can be quickly suppressed.
In the above embodiment, the operating capacity of the compressor 36 is decreased and the increasing capacity of the blower 26 is changed according to the temperature change rate Δtc. That is, as shown in Steps Q10 to Q40, when the temperature change rate Δtc is equal to or higher than +2 [° C./min], the operating capacity of the compressor 36 is reduced by 10 Hz, and the air blowing capacity of the blower 26 is increased by 500 rpm. When the temperature change rate Δtc is low (0 [° C./min] or more and less than +2 [° C./min]), the operating capacity of the compressor 36 is lowered and the width is reduced to 5 Hz, and the air blowing capacity of the blower 26 is increased. Is reduced to 250 rpm.

  It is predicted that the smaller the temperature change rate Δtc, the smaller the subsequent increase in the discharged refrigerant temperature tc. When the temperature change rate Δtc is small, the operating capacity of the compressor 36 is lowered and the raising capacity of the air blowing capacity of the blower 26 is reduced, thereby reducing the capacity of the heat pump 37, that is, the drying capacity, without significantly reducing the capacity of the compressor motor 36c. Temperature rise can be suppressed.

In addition, the adjustment of the driving ability according to the temperature change rate Δtc may be performed as necessary.
Regardless of the rate of change in temperature, the control in step Q20 (lowering the operating capacity of the compressor 36 and increasing the blowing capacity of the blower 26) may be executed uniformly.
In step R50 in FIG. 7 and step T50 in FIG. 8, contrary to step Q20 in FIG. 6, control is performed to increase the operating capacity of the compressor 36 and decrease the air blowing capacity of the blower 26. Is that the discharge refrigerant temperature tc and the temperature change rate Δtc are both lower than expected, it is determined that the capability of the heat pump 37 is still low and the capability of the heat pump 37 is increased.

  In addition, when changing the operating frequency of the compressor 36 and the rotational speed of the blower 26 (step Q20, step Q40, step R50, step T50, etc.), the current operating frequency and the rotational speed are each continued for 2 minutes. Changes may be made to the conditions, and they may not be changed when they are not continued for 2 minutes. In this way, the operation frequency and the number of rotations are not frequently changed at a short time interval such as the predetermined time (0.5 minutes) interval in step S40.

  Moreover, in the said embodiment, the control apparatus 50 may be provided with the heat pump abnormal stop function. This heat pump abnormality stop function is a function of stopping the operation of the heat pump 37 when the discharged refrigerant temperature tc rises to a preset abnormality determination temperature (a temperature higher than the predetermined temperature).

Next, FIGS. 10 to 16 show a second embodiment. In the second embodiment, an automatic expansion valve 61 is provided as a throttle means, and the automatic expansion valve 61 is controlled in addition to the compressor 36 and the blower 26 in accordance with the discharge refrigerant temperature. Different.
The automatic expansion valve 61 is configured such that the opening (throttle) can be adjusted by a pulse motor, and receives a pulse from the control device 50 as an opening adjustment signal. For example, it is fully opened with 500 pulses. In FIG. 12 corresponding to FIG. 5 of the first embodiment, step S10a, step S30a, step S80a, step S100a, step S120a, and step S130a are different from the first embodiment. In step S10a, the operating frequency of the compressor 36 is set to an initial value of 60 Hz, the rotational speed of the blower 26 is set to an initial value of 4000 rpm in advance, and the initial value of the opening of the automatic expansion valve 61 is set to 300. Set to pulse.

In step S30a, the compressor 36 and the blower 26 are operated, and the automatic expansion valve 61 is opened at an opening corresponding to 300 pulses in this case.
In FIG. 13 showing the control content of step S80a, step Q20a, step Q40a, and step Q50a are different from the first embodiment (FIG. 6). In step Q20a, the operating frequency of the compressor 36 is lowered by 10 Hz and the rotational speed of the blower 26 is increased by 500 rpm (similar to step Q20), and the opening of the automatic expansion valve 61 is increased by 15 pulses. As the opening degree of the automatic expansion valve 61 increases (the degree of throttling decreases), the refrigerant pressure on the discharge side of the compressor 36 decreases and the load decreases.

As a result, in addition to the decrease in the operating capacity of the compressor 36 and the increase in the blowing capacity of the blower 26, the opening degree of the automatic expansion valve 61 increases, so that the operating capacity of the heat pump 37 further decreases and the temperature of the compressor motor 36c increases. The rise can be suppressed and a temperature drop can be expected.
Further, in step Q40a, the compressor 36 and the blower 26 are operated in the same manner as in step Q40 of the first embodiment, and the opening of the automatic expansion valve 61 is increased by an amount equivalent to 7 pulses. In this case as well, the temperature of the winding 36f can be further lowered by the amount by which the opening degree of the automatic expansion valve 61 is increased.

In step Q50a, the operating capacity of the compressor 36 and the blower 26 is not changed as in step Q50, and the opening degree of the automatic expansion valve 61 is not changed.
In FIG. 14 which shows the control content of step S100a (FIG. 12), step R20a, step R40a, and step R50a are different from the first embodiment (FIG. 7). In step R20a, step R40a, and step R50a, the compressor 36 and the blower 26 perform superheat control on the opening degree of the automatic expansion valve 61 in addition to performing the same operation capability control as in steps R20, R40, and R50, respectively. Adjust by.

  This superheat control does the following: The evaporator outlet refrigerant temperature sensor 47 and the evaporator inlet refrigerant temperature sensor 46 capture the inlet / outlet refrigerant temperature data of the evaporator 34, determine the superheat amount from the temperature difference (exit refrigerant temperature-inlet refrigerant temperature), and The opening degree of the automatic expansion valve 61 (the amount of refrigerant supplied to the evaporator 34) is adjusted so that the superheat target temperature is reached. As a result, the amount of refrigerant supplied to the evaporator 34 is optimized.

  Further, in FIG. 15 showing the control content of step S120a (FIG. 12), step T20a, step T40a, and step T50a are different from the first embodiment (FIG. 7). In Step T20a, Step T40a, and Step T50a, the compressor 36 and the blower 26 perform the same operation capability control as in Step T20, Step T40, and Step T50, respectively, and the opening degree of the automatic expansion valve 61 is set as described above. Adjust by heat control.

In addition, each control value of the compressor 36, the air blower 26, and the automatic expansion valve 61 in this 2nd Embodiment, and the control form of the automatic expansion valve 61 are shown in FIG.
In the second embodiment, in addition to a reduction in the operating capacity of the compressor 36 and an increase in the blowing capacity of the blower 26, the operating capacity of the heat pump 37 is further reduced by increasing the opening degree of the automatic expansion valve 61, and compression is performed. An increase in temperature of the machine motor 36c can be suppressed, and a decrease in temperature can also be expected.

  Next, FIGS. 17 to 23 show a third embodiment. In the third embodiment, a compressor blower 71 for air-cooling the compressor 36 is provided, and the compressor blower 71 is controlled in addition to the compressor 36 and the blower 26 according to the discharge refrigerant temperature. This is different from the first embodiment. The compressor blower 71 includes a compressor blower motor 72 and blades 73, and is provided at a position where the compressor 36 can be cooled. The compressor blower 71 has a configuration in which the predetermined rotation speed switching control is not performed, and the blades 73 rotate at a substantially constant rotation speed.

  In FIG. 19 corresponding to FIG. 5 of the first embodiment, step S80b, step S100b, step S120b, and step S130b are different from the first embodiment. In FIG. 20 which shows the control content of step S80b, step Q20b, step Q40b, and step Q50b differ from 1st Embodiment (FIG. 6). In step Q20b, in addition to lowering the operating frequency of the compressor 36 by 10 Hz and increasing the rotational speed of the blower 26 by 500 rpm (similar to step Q20), the compressor blower 71 is operated (increase the blowing capacity). In addition to a reduction in the operating capacity of the compressor 36 and an increase in the blowing capacity of the blower 26, the operation of the blower 71 for the compressor directly cools the compressor 36, thereby suppressing the temperature increase of the compressor motor 36c. The temperature rises further and a rapid temperature drop can be expected.

Further, in step Q40b, the compressor blower 71 is operated in addition to performing the same operation capacity control as the step Q40 of the first embodiment for the compressor 36 and the blower 26. Also in this case, the temperature of the winding 36f can be further lowered.
Further, in step Q50b, the compressor 36 and the blower 26 are not changed in operating capacity in the same manner as in step Q50, and the compressor blower 71 is not operated (the blowing capacity is lowered, in this case, the operation is stopped).

  In FIG. 21 showing the control content of step S100b (FIG. 19), step R20b, step R40b, and step R50b are different from those in the first embodiment (FIG. 7). In step R20b, step R40b, and step R50b, the compressor 36 and the blower 26 are not operated as the compressor blower 71 in addition to performing the same operation capability control as that in steps R20, R40, and R50, respectively.

  Further, in FIG. 22 showing the control content of step S120b (FIG. 19), step T20b, step T40b, and step T50b are different from the first embodiment (FIG. 7). In step T20b, step T40b, and step T50b, the compressor 36 and the blower 26 are not operated in the compressor blower 71 in addition to performing the same operation capability control as in steps T20, T40, and T50, respectively.

In addition, each adjustment value or control form of the compressor 36, the air blower 26, and the air blower 71 for compressors in this 3rd Embodiment is shown in FIG.
In the third embodiment, in addition to reducing the operating capacity of the compressor 36 and increasing the blowing capacity of the blower 26, the compressor motor 36c is further operated by operating the compressor blower 71 (increasing the blowing capacity). Temperature rise can be suppressed, and a temperature drop can also be expected.

Although the control of the blowing capacity of the compressor blower 71 is switching between operation and stop, the rotation speed may be switched.
In each of the above embodiments, a washing / drying machine is shown, but a clothes drying machine having only clothes drying may be used. The predetermined temperature may be changed as appropriate. Also, the adjustment value of the compressor operating capacity and the adjustment value of the air blowing capacity of the blower may be appropriately changed.

  The clothes dryer according to the embodiment described above includes an outer box, a drying chamber provided in the outer box and having an exhaust port and an air supply port, and the exhaust port and the air supply port provided outside the drying chamber. A circulation air passage communicating with the air, a blower provided in the circulation air passage and circulating the air in the circulation air passage, a compressor comprising a winding of a compressor motor made of aluminum wire, a condenser A refrigerating cycle in which a condenser, a throttle means, and an evaporator are connected in a closed loop with a refrigerant pipe, the evaporator is provided in the circulation air passage, and the condenser is provided in the circulation air passage from the evaporator. A heat pump provided on the downstream side with respect to the air flow, a discharge refrigerant temperature sensor for detecting the temperature of refrigerant discharged from the compressor, and a temperature detected by the discharge refrigerant temperature sensor equal to or higher than a predetermined temperature set in advance Before when And a control means for controlling to increase the blowing capacity of the blower as well as reduce the operating capacity of the compressor. According to this, an excessive temperature rise of the compressor motor can be suppressed without interrupting the drying operation, and extension of the drying time due to the interruption of the drying operation can be prevented as much as possible.

  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 drawings, 1 is an outer case of the washing / drying machine according to the embodiment, 2 is a water tank, 3 is a drum, 3a is a drying chamber, 12 is a hot air introduction port, 13 is an exhaust port, 14 is an air supply port, and 22 is a ventilation duct. , 26 is a blower, 31 is a circulation air passage, 34 is an evaporator, 35 is a condenser, 36 is a compressor, 36c is a compressor motor, 36f is a winding, 37 is a heat pump, and 43 is a capillary tube (throttle means). , 44 is an exhaust temperature sensor, 45 is a supply air temperature sensor, 46 is an evaporator inlet refrigerant temperature sensor, 47 is an evaporator outlet refrigerant temperature sensor, 48 is a discharge refrigerant sensor, 49 is a refrigeration cycle, 61 is an automatic expansion valve (throttle) Means), 71 denotes a compressor blower.

Claims (3)

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 communicating with the exhaust port and the air supply port;
A blower provided in the circulation air passage to circulate the drying chamber and the air in the circulation air passage;
The compressor motor winding is composed of an aluminum wire, a compressor, a condenser, a throttling means, and a refrigeration cycle in which an evaporator is connected in a closed loop with a refrigerant pipe, and the evaporator is disposed in the circulation air passage. A heat pump provided on the downstream side of the evaporator with respect to the flow of air in the circulation air passage; and
A discharge refrigerant temperature sensor for detecting a temperature of refrigerant discharged from the compressor;
Control means for performing control to reduce the operating capacity of the compressor and increase the blowing capacity of the blower when the temperature detected by the discharged refrigerant temperature sensor is equal to or higher than a predetermined temperature set in advance;
With clothes dryer. The throttling means is composed of an automatic expansion valve capable of adjusting the opening based on a command from the control means,
The control means reduces the operating capacity of the compressor and increases the blowing capacity of the blower when the temperature detected by the discharged refrigerant temperature sensor is equal to or higher than a predetermined temperature set in advance. The clothes dryer according to claim 1, wherein control is performed to increase the opening of the clothes. A compressor blower for air-cooling the compressor;
The control means reduces the operating capacity of the compressor and increases the blowing capacity of the blower when the temperature detected by the discharged refrigerant temperature sensor is equal to or higher than a predetermined temperature set in advance. The clothes dryer of Claim 1 which performs control which enlarges the ventilation capability of an air blower.

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