WO2008018384A1

WO2008018384A1 - Dryer

Info

Publication number: WO2008018384A1
Application number: PCT/JP2007/065265
Authority: WO
Inventors: Hirokazu Ohe; Takeo Noguchi; Susumu Kitamura; Shohzoh Tanaka; Minoru Matsuse; Takashi Tsujimoto
Original assignee: Sharp Kabushiki Kaisha
Priority date: 2006-08-10
Filing date: 2007-08-03
Publication date: 2008-02-14
Also published as: JP2008062025A

Abstract

A dryer producing less noise and having high efficiency. A washing/drying machine (200) has a rotating drum (230) for receiving a wash, a warm air route section (241) for causing gas to flow into the inside of the rotating drum (230), a moist air route section (242) for causing the gas to flow out of the inside of the rotating drum (230), a high-temperature-side heat exchange section (420) for heating the gas flowing in the warm air route section (241), a low-temperature-side heat exchange section (430) for cooling the gas flowing in the moist air route section (242), and a Stirling engine (410) including a heat production head (411) and a heat absorption head (412). The high-temperature-side heat exchange section (420) exchanges heat so as to heat the gas by the heat production head (411) of the Stirling engine (410), and the low-temperature-side heat exchange section (430) exchanges heat so as to cool the gas by the heat absorption head (412) of the Stirling engine (410).

Description

Specification

Dryer

Technical field

[0001] The present invention relates to a dryer.

Background art

[0002] In recent years, there has been an increasing demand for washing and drying machines for washing clothes and the like from washing to drying! In particular, if you want to dry a small amount of laundry immediately, reduce the time to dry outdoors or indoors, or if you cannot wash during the day, you can wash your clothes at night and dry it after dehydration. Therefore, the convenience that matches the user's lifestyle is appreciated!

[0003] In such a washing and drying machine, conventionally used laundry drying methods generally use a heating means such as an electric heater or gas while rotating a rotating tub containing a laundry containing moisture. Drying is performed by supplying heated warm air. For example, in a water-cooled dehumidifying drier described in Japanese Patent Application Laid-Open No. 63-122500 (Patent Document 1), high-humidity air during and / or after drying can be exhausted as it is. Or, it is cooled and dehumidified by air or tap water outside the machine, and it is recirculated by air cooling or water-cooled and heat exchange dehumidified and then returned to the heating means.

[0004] Generally, in order to shorten the drying time of laundry, for example, the amount of power consumption increases in proportion to the power that can be considered to increase the heat capacity of a heating means such as a heater.

[0005] In addition, if heat exchange dehumidification with cooling water is used, a large amount of water is used, and water consumption increases in proportion to the drying time.

[0006] In view of this, for example, in Japanese Patent Laid-Open No. 60-220097 (Patent Document 2), in order to reduce the power consumption and the amount of water used, a heat pump device is provided in the circulation path of air used for drying laundry. A drying method has also been proposed in which a condenser (corresponding to the heating means described above) and an evaporator (corresponding to the cooling and dehumidifying means described above) are provided and heat and cold are effectively used. According to this drying method using a heat pump, air can be heated and cooled and dehumidified without using a heater or water, so that power consumption can be reduced and water can be saved.

[0007] JP 2004-215943 (Patent Document 3) and JP 2005-40316 (Patent text) For item 4), a heat pump is used that stabilizes a safe state by preventing the amount of heat of the circulating air from increasing by exhausting the circulating air in the air circulation path used to dry clothes. A clothes dryer and a dryer with a washing function are listed!

[0008] Japanese Unexamined Patent Publication No. 2006-212117 (Patent Document 5) describes a clothes drying apparatus that continues the operation of a compressor when a drying operation is interrupted in a clothes dryer using a heat pump. . Also, JP 2006-61353 A (Patent Document 6) describes a clothes drying apparatus using a heat pump that stops the operation of the compressor for a predetermined time after the drying operation is interrupted. Has been. By doing so, the load on the compressor is reduced when the drying operation and the interruption of the drying operation are repeated in a short time, and the return of the hot air temperature by the heat pump device is accelerated.

[0009] Japanese Patent Application Laid-Open No. 2006-272024 (Patent Document 7) and Japanese Patent Application Laid-Open No. 2005-261703 (Patent Document 8) disclose that a compressor is started in advance before entering a drying process. A washing and drying machine using a heat pump is described which reduces the time required for the drying process.

Patent Document 1: Japanese Patent Laid-Open No. 63-122500

Patent Document 2: Japanese Patent Laid-Open No. 60-220097

Patent Document 3: Japanese Patent Application Laid-Open No. 2004-215943

Patent Document 4: Japanese Unexamined Patent Application Publication No. 2005-40316

Patent Document 5: Japanese Unexamined Patent Publication No. 2006-212117

Patent Document 6: Japanese Unexamined Patent Publication No. 2006-61353

Patent Document 7: Japanese Unexamined Patent Publication No. 2006-272024

Patent Document 8: Japanese Unexamined Patent Application Publication No. 2005-261703

Disclosure of the invention

Problems to be solved by the invention

[0010] However, even in a drying method using a heat pump, since a compression means such as a compressor is newly used to compress the refrigerant, noise and vibration are generated during operation, and noise during drying increases. Problems arise. In addition, depending on the type of refrigerant used in the compressor, there is a problem that the cost after disposal is high. In addition, from the perspective of preventing global warming, it will be necessary to reduce the power consumption of electrical products in the future. Even in the case of dryers and laundry dryers, improvements in drying functions and reductions in power consumption are required.

[0011] When a heat pump is used in the dryer, the heat amount of the circulating air is increased by driving the heat pump, the temperature of the heat pump refrigerant itself is increased, and the temperature of the refrigerant is increased and the pressure is increased. It is extremely difficult to significantly reduce the power output that can limit the output of the heat pump by inverter control, etc. Even if the amount of heat of the circulating air is excessive, it is difficult to reduce the amount of heat applied. In addition, in order to compress and liquefy a high-temperature and high-pressure refrigerant, the load on the heat pump increases. Therefore, the dryers described in Japanese Patent Application Laid-Open No. 2004-215943 (Patent Document 3) and Japanese Patent Application Laid-Open No. 2005-40316 (Patent Document 4) are power pumps that exhaust the circulating air with a high amount of heat to the outside. Unnecessary amount of heat generated by the steam or steam contained in the circulating air is discharged into the room where the dryer is installed, which may increase the amount of heat in the entire room or cause condensation due to the discharged steam. is there.

[0012] In a clothes dryer using a heat pump, until the pressure state of the refrigerant in the pipe settles to an equilibrium state when the drying operation is interrupted, and until the refrigerant is vaporized and liquefied when the drying operation is resumed. Takes time. Therefore, when the drying operation is resumed in a short time after the interruption of the drying operation, the drying operation is interrupted as in the clothes dryer described in JP 2006-212117 A (Patent Document 5). Nevertheless, it is necessary to continue driving the compressor, which consumes wasted power and puts a heavy burden on the compressor. On the other hand, when the drying operation is interrupted as in the clothes dryer described in Japanese Patent Laid-Open No. 2006-61353 (Patent Document 6), if the compressor is not operated for a certain period of time, the drying operation is performed. The drying operation cannot be resumed in a short time after the operation is interrupted.

[0013] Further, like the washing and drying machine described in Japanese Patent Application Laid-Open No. 2006-272024 (Patent Document 7) and Japanese Patent Application Laid-Open No. 2005-261703 (Patent Document 8), a compressor is previously set before entering the drying process. Doing so will generate unnecessary heat and noise, and increase power consumption.

Five.

[0014] Therefore, an object of the present invention is to provide a dryer with low noise and high efficiency!

Yes Means for solving the problem

[0015] A dryer according to the present invention includes a container for storing an object to be dried, a circulation path for allowing a gas to flow into the container, and a gas discharged from the container inside the container. A circulation path for allowing the gas flowing in the circulation path, a first heat exchange section for heating the gas flowing through the circulation path, a second heat exchange section for cooling the gas flowing through the circulation path, and a heating head And a Stirling engine including a heat absorption head, the first heat exchange section performs heat exchange so as to heat the gas with the heat generation head of the Stirling engine, and the second heat exchange section includes the Stirling engine. Heat exchange is performed so that the gas is cooled by the endothermic head of the engine.

Conventionally, in a heat pump used in a dryer, heat is generated by a condensing unit that compresses a refrigerant by a compressor to change from gas to liquid, and an evaporation unit that expands the refrigerant to change from liquid to gas. We are exchanging. That is, in the heat pump, the refrigerant moves from the condensing unit through the pipe or the like to the evaporation unit and changes from liquid to gas, and from the evaporation unit through the pipe or the like to the condensing unit, from gas to liquid. It is necessary to repeat changing.

[0017] On the other hand, the Stirling engine compresses a working gas such as helium in the compression space by reciprocating the displacer in the cylinder to heat the heat generating head, and expands the heat generating head in the expansion space. Cooling. Thus, in the Stirling engine, the working gas remains in a gaseous state and moves only between the compression space and the expansion space. For example, the compression space and the expansion space are arranged at both ends of one cylinder. In this case, the working gas reciprocates from one end of the cylinder to the other end while maintaining the gaseous state. .

[0018] Thus, in the Stirling engine, since it is not necessary to change the state of the refrigerant between the gas and the liquid, the responsiveness of the Stirling engine is higher than that of the heat pump. For example, the time required from the start of driving the Stirling engine until the heat generating head and the heat absorbing head reach a predetermined temperature is the same as the time when the evaporation unit and the condensing unit are at a predetermined temperature after the heat pump is started. It is shorter than the time required to become.

[0019] Therefore, by using a Stirling engine, it is not necessary to start up for a long time before or at the start of the drying operation. Energy efficient, that is, a dryer that can effectively reduce energy consumption and save energy. In this way, a dryer equipped with a Stirling engine can shorten the time required to start the dryer, and the time required to start again after interrupting the operation once during the operation of the dryer. Can be shortened

[0020] Further, the Stirling engine has a wider output control range than the heat pump. Inverter compressors used in heat pumps can control output in the range of 30% to 100%, but in Stirling engines, theoretically, output can be controlled in the range of 0% to 100%. I can do it. For this reason, the excess heat of the circulating air is not increased excessively from the latter stage to the final stage of the drying process, so there is no need to exhaust the circulating air to the outside.

[0021] Further, the vibration system of the heat pump used in the conventional dryer is a complicated vibration system including rotation vibration because a compressor is used for compression and expansion of the refrigerant. On the other hand, a Stirling engine has a simple vibration system compared to a heat pump. That is, in a Stirling engine, only a linear motion of reciprocation of a piston and a displacer is performed.

[0022] As described above, the Stirling engine has a simple vibration system, and therefore can easily absorb vibration. For example, vibration can be easily suppressed by providing a vibration absorbing member such as a panel having the co-frequency of the displacer vibration as the natural frequency. In a Stirling engine, vibration can be easily suppressed, so noise due to vibration is less likely to occur.

[0023] By doing so, vibration and noise can be reduced, and usability that does not deteriorate the indoor environment in which the dryer is installed, that is, use and saving immediately. Energy, that is, energy consumption can be effectively reduced, and a dryer that can easily save energy can be provided.

[0024] The dryer according to the present invention is provided so as to cover the container, and includes a water tank for containing water. The container is rotatably supported in the water tank and is accommodated inside the container. It is structured so that the object to be dried can be washed in the container! Are preferred.

[0025] By doing in this way, it is possible to quickly dry after washing. In addition, the Stirling engine is a simple structure that can generate cold heat with a Stirling engine alone that requires a compressor and refrigerant piping used for heat pumps. In addition, it is possible to provide a highly reliable dryer that is unlikely to fail even when the dryer vibrates.

In the dryer according to the present invention, it is preferable that the heat generating head is arranged in the circulation path to constitute the first heat exchange unit. In addition, it is preferable that the endothermic head is disposed in the circulation path and constitutes a second heat exchange section.

[0027] By doing so, a heat transfer path from the heat generating head to the first heat exchanging part or a cold air transfer path from the heat absorbing head to the second heat exchanging part becomes unnecessary, and It is possible to reduce the number of parts and make it easy to manufacture a heating and dehumidifying device, as well as a heat transfer path from the heat generating head to the first heat exchanging part, or a cool air transfer from the heat absorbing head to the second heat exchanging part. It is possible to provide a highly reliable dryer that can prevent damage to piping due to vibration in the route.

[0028] In the dryer according to the present invention, the heat generating head is disposed in the circulation path to constitute the first heat exchanging portion, and the heat absorption head is disposed in the circulation path, It is preferable to configure the heat exchange section.

[0029] By doing so, it is necessary to provide a path for transmitting the heat generated by the heat generating head to the first heat exchanging section and a path for transmitting the cold air generated by the heat absorbing head to the second heat exchanging section. Even when the dryer vibrates during washing, especially when dehydration increases in vibration, a path for transferring the heat generated by the heat generating head to the first heat exchanging section and the cold air generated by the heat absorbing head are transferred to the second heat exchanging section. The ability to provide a highly reliable dryer with no damage to the transmission path.

[0030] The dryer according to the present invention includes a connecting pipe disposed between the heat generating head and the heat absorbing head, and the connecting pipe is disposed coaxially with the heat generating head and the heat absorbing head, and is connected to the heat generating head and the heat absorbing head. It is preferable that the head and connecting pipe are placed in the circulation path.

[0031] By doing this, the circulation path can be shortened to suppress pressure deficits, The force S reduces the heat effect between the heat generating head and the heat absorbing head by the air layer around the connecting pipe.

The invention's effect

[0032] As described above, according to the present invention, vibration and noise are small, and the indoor environment in which the dryer is installed does not deteriorate, and the usability is high. A highly reliable dryer can be provided.

Brief Description of Drawings

FIG. 1 is a perspective view schematically showing an overall appearance of a washing / drying machine as Embodiment 1-1 of the present invention.

FIG. 2 is a side sectional view schematically showing a cross section of the washing / drying machine of FIG. 1 as viewed from the direction of line II-II.

FIG. 3 is a cross-sectional view showing an overall cross section of a Stirling engine.

FIG. 4 is a perspective view showing the entire body of the heating and dehumidifying device.

FIG. 5 is a cross-sectional view showing an outline when the washing / drying machine is viewed from the direction of the line VV in FIG.

FIG. 6 is a side sectional view schematically showing a side section of a washing / drying machine as Embodiment 1-2 of the present invention.

FIG. 7 is a cross-sectional view schematically showing a cross section of the washing / drying machine as viewed from the back.

FIG. 8 is a perspective view showing another embodiment of the main body of the heating and dehumidifying device provided in the washing and drying machine as Embodiment 1-3 of the present invention.

FIG. 9 is a perspective view showing another embodiment of the main body of the heating and dehumidifying device provided in the washing and drying machine as Embodiment 14 of the present invention.

FIG. 10 is a cross-sectional view showing the configuration of the water supply / drainage system of the drum type washer / dryer according to Embodiment 21 of the present invention.

FIG. 11 is a cross-sectional view showing a configuration of a drying processing system of a drum-type washing / drying machine according to Embodiment 21 of the present invention.

FIG. 12 is an enlarged view of the main part of FIG.

FIG. 13 is a schematic view of a clutch mechanism in a disengaged state.

FIG. 14 is a schematic diagram of the coupling state of the clutch mechanism and the power transmission mechanism as seen from A in FIG. FIG. 15 is an enlarged view of a main part showing a 0 ° rotation state of the crankshaft.

FIG. 16 is an enlarged view of a main part showing a 90 ° rotation state of the crankshaft.

17] This is an enlarged view of the main part showing a 180 ° rotation state of the crankshaft.

18] This is an enlarged view of the main part showing the 270 ° rotation state of the crankshaft.

19] A longitudinal sectional view of a washing and drying machine according to Embodiment 2-2 of the present invention.

20] It is an enlarged view of the main part of FIG.

FIG. 21 is a sectional view taken along line BB in FIG.

22] It is a schematic diagram of the clutch mechanism in a disengaged state.

FIG. 23 is a CC cross-sectional view of FIG.

Fig. 24] is an enlarged view of the main part showing a state in which the crankshaft has rotated 90 ° from the state of Fig. 23. Fig. 25] is an enlarged view of the main part showing a state in which the crankshaft has been rotated 180 ° from the state of Fig. 23.

Fig. 26] is an enlarged view of the main part showing a state in which the crankshaft has been rotated 270 ° from the state of FIG.

27] It is a longitudinal sectional view of a washing and drying machine according to Embodiment 2-3 of the present invention.

28] It is an enlarged view of the main part of FIG.

FIG. 29 is a sectional view taken along the line DD of FIG. 28.

FIG. 30 is a schematic diagram of the clutch mechanism in a disengaged state.

31] It is a cross-sectional view of the main parts of the connecting gear and slide gear, (a) is a top view of the slide gear, (b) is a view from arrow F in (a), (c) is a view from arrow G in (a) (D) is a top view of the transmission gear, (e) is a view taken in the direction of arrow H in (d), (f) is a sectional view taken along line II in (e), (g) is a sectional view taken along line JJ in (e), h) is a KK cross-sectional view of (e), and (i) is a LL cross-sectional view of (e).

FIG. 32 is a cross-sectional view taken along the line EE in FIG.

Fig. 33] Enlarged view of the main part showing the crankshaft rotated 90 ° from the state of Fig. 32. Ord 34] Enlarged view of the main portion showing the crankshaft rotated 180 ° from the state of Fig. 32. is there.

FIG. 35 is an enlarged view of essential parts showing a state where the crankshaft has been rotated 270 ° from the state of FIG. 32.

FIG. 36 is a diagram showing a temporal change in temperature on the high temperature side measured immediately after the start of driving of the Stirling engine and the heat pump.

FIG. 37 is a diagram showing a temporal change in temperature on the high temperature side from the start of driving of the Stirling engine and the heat pump until reaching a predetermined temperature.

FIG. 38 is a diagram showing the time change of the temperature that changes in 10 seconds with respect to the temperature on the high temperature side measured immediately after the start of driving of the Stirling engine and the heat pump.

[Fig.39] Changes in the temperature of the high and low temperatures of the Stirling engine and the high and low temperatures of the heat pump measured at 10-second intervals immediately after the start of driving the Stirling engine and heat pump. FIG.

Explanation of symbols

[0034] 3: Water tank, 5: Drum, 24, 48: Heat exchange section, 25, 41: Ventilation path, 38a, 54a: Heat absorption head, 38b, 54b: Heat generation head, 100: Stirling engine, 148: Regenerator tube 200, 300: Washing and drying machine, 220: Water tank, 230: Rotating drum, 241: Hot air path section, 242: Wet air path section, 243: Circulation path section, 247: Hot air path section in the tank, 248: Water tank Internal wet air passage section, 410, 6 10, 710: Stirling engine, 411, 611, 711: Heat generation head, 412, 612, 712: Heat absorption head, 420, 620, 720: High temperature side heat exchange section, 430, 630 , 730: Low temperature side heat exchanger. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

[0036] (Embodiment 1 1)

FIG. 1 is a perspective view schematically showing the overall appearance of a washing / drying machine as Embodiment 1-1 of the present invention, and FIG. 2 shows the washing / drying machine of FIG. 1 as viewed from the direction of line II-II. FIG. 6 is a side sectional view schematically showing a cross section.

[0037] As shown in FIGS. 1 and 2, the washing and drying machine 200 includes a main body 210, a water tank 220 attached to the inside of the main body 210, and a container for storing laundry as an object to be dried. As an aquarium

220, and a rotating drum 230 rotatably supported within 220. An outer door 201 is attached to the front surface of the main body 210. An inner door 203 is attached inside the outer door 201. By opening the outer door 201 and opening the inner door 203, the laundry can be put into or taken out of the rotary drum 230 through the laundry inlet 202 provided on the front surface of the main body 210. By closing the outer door 201 and closing the outer door 201, the laundry input port 202 can be closed. The inner door 203 has a central portion made of transparent glass so that the inside of the rotary drum 230 can be seen, and has a recessed bowl shape or a so-called basin shape. A door packing 204 made of an elastic material such as rubber is fitted and fixed to the peripheral wall of the water tank 220 on the laundry input port 202 side. When the inner door 203 is closed, the door packing 204 is brought into close contact with the peripheral edge of the inner door 203 so that the water tank 220 is sealed.

The rotating drum 230 is supported so as to rotate around the shaft portion 231 inside the water tank 220. In this way, the drum type washing and drying machine 200 has a double structure composed of the water tank 220 and the rotating drum 230. The rotary drum 230 includes a drum body 232 that forms an inner peripheral wall surface at the center in the rotation axis direction, a drum lid 233 that forms an opening at one end, and a drum bottom 234 that forms an inner bottom wall surface at the other end. Generally, it is made from stainless steel plate. An uneven surface such as a rib is formed on the drum bottom 234 by pressing to attach a structural component such as the shaft 231 and support a desired load, thereby improving the strength of the bottom wall surface. A number of small holes 235 for water supply, drainage, and ventilation are provided in the peripheral wall and bottom of the rotary drum 230. A fluid balancer 205 is fixed to the outer peripheral edge of the drum lid 233 to prevent vibration during rotation. The shaft portion 231 includes a shaft of a drum rotation drive motor 236 for rotating the rotary drum 230. The rotation of the drum rotation drive motor 236 is controlled by an inverter circuit. The water tank 220 is elastically supported by a coil spring (not shown) from the upper part and by an anti-vibration damper (not shown) from the lower part. A water supply path 209 connected to tap water is disposed above the water tank 220, and is connected to the water tank 220 via the detergent case 207. A water supply valve 208 is provided in the middle of the water supply route 209, and the supply of tap water to the water tank 220 is controlled by opening and closing the water supply valve 208. A drain valve 206 is provided at the bottom of the water tank 220, and washing liquid and the like can be drained from the water tank 220 to the outside of the main body 210 by opening and closing the drain valve 206. FIG. 3 is a cross-sectional view showing an entire cross section of the Stirling engine.

As shown in FIG. 3, the cylinders 110 and 111 are central to the assembly of the Stirling engine 100. The axes of the cylinders 110 and 111 are aligned on the same line. A piston 112 is inserted into the cylinder 110 and a displacer 113 is inserted into the cylinder 111. During operation of the Stirling engine 100, the piston 112 and the displacer 113 reciprocate without contacting the inner surfaces of the cylinders 110 and 111 by the gas bearing mechanism. The piston 112 and the displacer 113 move with a predetermined phase difference.

A cup-shaped magnet holder 114 is provided at one end of the piston 112. A displacer rod 115 projects from one end of the displacer 113. The displacer rod 115 passes through the piston 112 and the magnet holder 114 so as to slide freely in the axial direction.

The cylinder 110 holds the linear motor 120 outside the portion corresponding to the operation region of the piston 112. The linear motor 120 is inserted into an outer space J yoke 122 having an inner 121, an inner yoke 123 provided in contact with the outer peripheral surface of the cylinder 110, and an annular space between the outer yoke 122 and the inner yoke 123. It has a ring-shaped magnet 124 and synthetic resin end brackets 125 and 126 that hold the outer yoke 122 and the inner yoke 123 in a predetermined positional relationship.

The central portion of the spring 130 is fixed to the hub portion of the magnet holder 114. The center portion of the spring 131 is fixed to the displacer rod 115. The outer periphery of the springs 130 and 131 is fixed to the end bracket 126. A spacer 132 is disposed between the outer peripheries of the springs 130 and 131, so that the springs 130 and 131 maintain a certain distance. The springs 130 and 131 are disc-shaped materials with spiral cuts, and the displacer 113 is resonated with a predetermined phase difference (ideally about 90 ° phase difference) with respect to the piston 112. To play a role.

[0045] A heat generating head 140 and a heat absorbing head 141 are arranged outside the portion of the cylinder 111 corresponding to the operating region of the displacer 113. The heat generating head 140 has a ring shape and the heat absorbing head 141 has a cap shape, both of which are made of a metal having good heat conductivity such as copper or a copper alloy. The exothermic head 140 and the endothermic head 141 have ring-shaped internal heat exchangers 142 and 143 interposed, respectively. It is supported on the outside of the cylinder 111 in a round shape. Each of the internal heat exchangers 142 and 143 has air permeability, and transfers the heat of the working gas passing through the interior to the heat generating head 140 and the heat absorbing head 141.

A space surrounded by the heat generating head 140, the cylinders 110 and 111, the piston 112, the displacer 113, and the internal heat exchanger 142 becomes a compression space 145. The space surrounded by the heat absorbing head 141, the cylinder 111, the displacer 113, and the internal heat exchanger 143 becomes an expansion space 146.

A regenerator 147 is disposed between the internal heat exchangers 142 and 143. The regenerator 147 is a resin film wound in a cylindrical shape, and a number of minute protrusions are scattered on one side of the film to form a gap corresponding to the height of the protrusion between the films. It is supposed to be a path. The outside of the regenerator 147 is wrapped around the regenerator tube 148 force S, and an airtight passage is formed between the heat generating head 140 and the heat absorbing head 141. The heat generating head 140, the regenerator tube 148, and the heat absorbing head 141 are arranged coaxially. The regenerator tube 148 is an example of a connection tube.

[0048] A cylindrical pressure vessel 150 wraps the linear motor 120, the cylinder 110, and the piston 112.

The inside of the pressure vessel 150 becomes a back pressure space 151. On the peripheral surface of the pressure vessel 150, a terminal portion 152 for supplying electric power to the linear motor 120 and a pipe 153 for enclosing a working gas inside are arranged.

A dynamic vibration absorber 160 is attached to the outer surface of the pressure vessel 150. The dynamic vibration absorber 160 includes a shaft 161 protruding from the center of the end surface of the pressure vessel 150, a plate-like spring 162 fixed at the center of the shaft 161, and a mass (mass) 163 disposed on the periphery of the spring 162. . The spring 162 is a stack of a plurality of thin plate springs.

[0050] The Stirling engine 100 operates as follows. A magnetic field penetrating the magnet 124 is generated between the outer yoke 122 and the inner yoke 123 that supply an alternating current to the coil 121 of the linear motor 120, and the magnet 124 reciprocates in the axial direction. By supplying power at a frequency that matches the resonance frequency determined by the total mass of the piston system (piston 112, magnet holder 114, magnet 124, and spring 130) and the panel constant of the spring 130, the piston system is smooth. Start a sinusoidal reciprocating motion.

[0051] Displacer system (displacer 113, displacer rod 115, and spring 1 In 31), the resonance frequency determined by the total mass and the panel constant of the spring 131 matches the driving frequency of the piston 112.

[0052] By the reciprocating motion of the piston 112, compression and expansion are repeated in the compression space 145. As the pressure changes, the displacer 113 also reciprocates. At this time, a phase difference is generated between the displacer 113 and the piston 112 due to flow resistance between the compression space 145 and the expansion space 146. In this way, the displacer 113 having a free piston structure reciprocates in synchronization with the piston 112 with a predetermined phase difference.

[0053] By the above operation, a Stirling cycle is formed between the compression space 145 and the expansion space 146. In the compression space 145, the temperature of the working gas increases based on the isothermal compression change, and in the expansion space 146, the temperature of the working gas decreases based on the isothermal expansion change. For this reason, the temperature of the compression space 145 rises and the temperature of the expansion space 146 falls.

[0054] The working gas that moves between the compression space 145 and the expansion space 146 during operation passes through the internal heat exchangers 142, 143, and transfers the heat it has to the heat generating head 140 and the heat absorbing head 141. Since the working gas flowing from the compression space 145 into the regenerator 147 is hot, the heat generating head 140 is heated by calorie. Since the working gas flowing from the expansion space 146 into the regenerator 147 has a low temperature, the heat absorbing head 141 is cooled.

[0055] The regenerator 147 functions to pass only the working gas without transferring the heat of the compression space 145 and the expansion space 146 to the counterpart space. The hot working gas entering the regenerator 1 47 from the compression space 145 through the internal heat exchanger 142 gives the heat to the regenerator 147 when passing through the regenerator 147, and the expansion space 146 in a state where the temperature is lowered. Flow into. The low-temperature working gas that has entered the regenerator 147 from the expansion space 146 through the internal heat exchanger 143 recovers heat from the regenerator 147 when passing through the regenerator 147, and enters the compression space 145 in a state where the temperature has risen. Inflow. That is, the regenerator 147 serves as a heat storage means.

[0056] When the piston 112 and the displacer 113 reciprocate, vibration is generated in the Stirling engine 100, and the dynamic vibration absorber 160 suppresses this vibration.

FIG. 4 is a perspective view showing the entire main body of the heating and dehumidifying device.

[0058] As shown in FIG. 4, the main body of the heating and dehumidifying device 400 includes a Stirling engine 410, a high temperature side heat exchange unit 420 as a first heat exchange unit, and a low temperature side heat exchange unit as a second heat exchange unit. Four 30. The Stirling engine 410 has a heat generating head 411 and a heat absorbing head 412. The configuration and operation of the Stirling engine 410 are the same as those of the Stirling engine 100 shown in FIG. The high temperature side heat exchanging unit 420 has heating fins 421 connected to the heat generating head 411 as fins, and the low temperature side heat exchanging units 430 have cooling fins 431 connected to the heat absorbing head 412 as fins. The calo heat fins 421 and the cooling fins 431 are disk-shaped, and the central portions are directly connected to the heat generating head 411 and the heat absorbing head 412 respectively. The cooling fins 431, the calo heat fins 421, and the Stirling engine 410 are arranged so as to be aligned substantially in a straight line, and are integrated to constitute a heating and dehumidifying device 400. The heating and dehumidifying device 400 is composed of this main body, a warm air side path portion and a humid air side path portion shown in FIG.

As described above, in the heating and dehumidifying apparatus 400, the high temperature side heat exchanging unit 420 includes the heating fins 421 arranged to be in contact with the heat generating head 411, and the low temperature side heat exchanging unit 430 is configured to absorb the heat. It includes cooling fins 431 arranged to contact the thermal head 412.

[0060] By doing so, it is possible to efficiently exchange heat between the gas in the heating fin 421 and the cooling fin 431. Further, the heat dehumidifying device 400 can be reduced in size.

FIG. 5 is a cross-sectional view schematically showing the washing / drying machine as viewed from the direction of the V—V line in FIG.

As shown in FIGS. 2 and 5, a hot air path portion 241 and a humid air path portion 242 are arranged on the back side of the rotary drum 230 in the main body 210 of the washing and drying machine 200. . The hot air passage unit 241 and the wet air passage unit 242 communicate with the inside of the water tank 220 through an intake port 245 and an exhaust port 246, respectively. The hot air path section 241 and the wet air path section 242 are connected via a circulation path section 243 extending almost linearly below the water tank 220. The circulation path section 243 is provided with the main body of the heating and dehumidifying device 400 such that the cooling fin 431 is on the wet air path section 242 side and the heating fin 421 is on the hot air path section 241 side. Below the water tank 220, a blower mechanism 244 is disposed inside the wet air passage 242.

As shown in FIG. 2, a hot water path portion 247 in the water tank is provided between the inner peripheral wall surface of the water tank 220 and the outer peripheral wall surface of the drum 232 of the rotary drum 230. Further, the inner peripheral wall surface of the water tank 220, the drum body 232 and the drum bottom 234 of the rotating drum 230 form a wet water path section 248 in the water tank. An intake port and an exhaust port are provided at the bottom of the water tank 220. In addition, the exhaust port The air inlet may be provided on the front surface, the side surface, or the upper portion. As shown in FIG. 5, the exhaust port is connected to the circulation path part 243 via a humid air path part 242 provided outside the back surface of the water tank 220. A blower mechanism is disposed in the wet air passage 242. The main body of the heating and dehumidifying device 400 including a Stirling engine is disposed in the circulation path portion 243 extending substantially linearly. More specifically, the heat generating head 411, the heat absorbing head 412, and the regenerator tube 148 of the main body of the heating and dehumidifying device 400 are arranged in a substantially linear circulation path portion 243. The circulation path part 243 is connected to the intake port via a hot air path part 241 provided outside the back surface of the water tank 220. The two-dot chain arrow in Fig. 2 indicates the direction of wind flow. The hot water path section 247 in the water tank, the wet air path section 248, the wet air path section 242, the circulation path section 243, and the hot air path section 241 constitute a circulation path. The hot water path section 247 in the water tank, the wet air path section 248 in the water tank, the wet air path section 242, the circulation path section 243, and the hot air path section 241 are examples of the circulation path.

[0064] The washing step, the rinsing step, the dehydrating step and the drying step performed using the washing / drying machine 200 configured as described above will be described below in the order of steps.

[0065] First, the outer door 201 and the inner door 203 are opened, and after the laundry is loaded through the laundry loading port 202, the inner door 203 and the outer door 201 are closed. Put the detergent in the detergent case and operate the operation panel. As a result, the outer door 201 and the inner door 203 are locked, the water supply valve 208 is opened, and water is supplied to the water tank 220 through the water supply path 209 and the detergent case 207. When a water level sensor (not shown) detects that the water level in the water tank 220 has reached a predetermined value, the water supply valve 208 is closed, and the rotary drum 230 is rotated by the drum rotation drive motor 236. Rotated according to. In this way, the washing process is started.

[0066] Regarding the rotation chart of the rotating drum 230, the rotation speed, the rotation period, the inversion period are classified according to the washing process, the rinsing process, the dehydration process, the drying process, or according to the type and course of the laundry. A plurality of rotation charts having different values are set in advance. The rotation chart is selected by the user or programmed to be selected automatically.

[0067] When the process is completed, the drain valve 206 is opened and the washing liquid is discharged out of the main body. When draining is completed, the rotating drum 230 rotates at a high speed on the rotation chart for the intermediate dehydration process. An intermediate dehydration step is performed. In the intermediate dehydration process, the washing liquid contained in the laundry is discharged to the inner wall surface of the water tank 220 through the small holes 235 provided in the peripheral wall of the rotating drum 230 by the centrifugal force generated by the high-speed rotation of the rotating drum 230. The washing liquid flows down along the inner wall surface of the water tank 220 and is discharged out of the main body through the drain valve 206.

[0068] When the intermediate dehydration step is completed, the program proceeds to the rinsing step. After the drain valve 206 is closed, the water supply valve 208 is opened, and water is supplied to the water tank 220 through the detergent case. When a water level sensor (not shown) detects that the water level in the water tank 220 has reached a predetermined value, the water supply valve 208 is closed and the rotating drum 230 is rotated by the drum rotation drive motor 236 according to the rotation chart for the rinsing process. Is done. The intermediate dehydration process and the rinsing process are repeated several times, and then the final rinsing process is performed. In the final rinsing process, the water supply valve 208 is opened and water containing a soft finish is supplied to the aquarium 220.

[0069] When the final rinsing step is completed, the drain valve 206 is opened and the rinsing liquid is discharged out of the main body 210. When the drainage is completed, a final dewatering process is performed in which the rotating drum 230 is rotated at high speed according to the rotary chart for the final dewatering process. In the final dewatering step, the rinsing liquid contained in the laundry by centrifugal force due to the high-speed rotation of the rotating drum 230 is applied to the inner wall surface of the water tank 220 through the small holes 235 provided in the peripheral wall of the rotating drum 230 in the same manner as the intermediate dewatering step. Discharged.

[0070] When the final dehydration step is completed, the process proceeds to the drying step. In the drying process, the rotary drum 230 is rotated and the heating / dehumidifying device 400 and the air blowing mechanism unit 244 are driven.

[0071] When the Stirling engine 410 of the heating and dehumidifying device 400 is driven, heat is exchanged so that the gas is heated by the calorie heat fin 421 and the gas is cooled by the cooling fin 431! Heat exchange.

[0072] By driving the heating and dehumidifying device 400 and the air blowing mechanism 244, the gas heated by the force P heat fin 421 causes the hot air path portion 241 to be indicated by an arrow of a two-dot chain line in FIG. Then, the air flows into the water tank 220 from the air inlet 245 through the hot air passage section 247 in the water tank, and blows into the rotating drum 230 (FIG. 2) disposed inside the water tank 220. After the gas contacts the laundry in the rotating drum 230 (Fig. 2), it passes through the small hole 235 and goes outside the rotating drum 230. It flows out and is exhausted to the wet air passage section 242 through the exhaust port 246 formed in the lower part of the water tank 220. The gas exhausted to the wet air passage section 242 has a high humidity due to moisture contained in the laundry in the rotating drum 230. The gas containing moisture flows as shown by a one-dot chain line arrow in FIG. 5, returns to the cooling fin 431, is cooled by the cooling fin 431, and is dehumidified. Moisture removed from the gas is discharged from the main body 210 through the drain pipe (not shown) from below the cooling fin 431. The dehumidified gas returns to the calo heat fin 421 through the circulation path 243. The drying process is performed by repeating this cycle.

As described above, the washing / drying machine 200 includes the rotary drum 230 for storing the laundry, the hot air path portion 241 for allowing the gas to flow into the rotary drum 230, and the inside of the rotary drum 230. In order to cool the gas flowing through the wet air passage section 242, the high-temperature side heat exchanging section 420 for heating the gas flowing through the hot air passage section 241, and the wet air passage section 242. The low temperature side heat exchanging part 430 and the Stirling engine 410 including the heat generating head 411 and the heat absorbing head 412 are provided, and the high temperature side heat exchanging part 420 is configured to heat the gas with the heat generating head 411 of the Stirling engine 410. The heat exchange is performed, and the low temperature side heat exchange unit 430 performs heat exchange so that the gas is cooled by the heat absorption head 412 of the Stirling engine 410.

[0074] Conventionally, in a heat pump used in a dryer, heat is generated by a condensing unit that compresses a refrigerant by a compressor to change from gas to liquid, and an evaporation unit that expands the refrigerant to change from liquid to gas. We are exchanging. That is, in the heat pump, the refrigerant moves from the condensing unit through the pipe or the like to the evaporation unit and changes from liquid to gas, and from the evaporation unit through the pipe or the like to the condensing unit, from gas to liquid. It is necessary to repeat changing.

[0075] On the other hand, the Stirling engine reciprocates the displacer in the cylinder, thereby compressing a working gas such as helium in the compression space to heat the heat generating head and expand the heat dissipating head in the expansion space. Cooling. Thus, in the Stirling engine, the working gas remains in a gaseous state and moves only between the compression space and the expansion space. For example, the compression space and the expansion space are arranged at both ends of one cylinder. In this case, the working gas remains in a gaseous state and is between one end of the cylinder and the other end. Go back and forth.

Thus, in the Stirling engine, since it is not necessary to change the state of the refrigerant between the gas and the liquid, the responsiveness of the Stirling engine is higher than that of the heat pump. For example, the time required from the start of driving the Stirling engine until the heat generating head and the heat absorbing head reach a predetermined temperature is the same as the time when the evaporation unit and the condensing unit are at a predetermined temperature after the heat pump is started. It is shorter than the time required to become.

[0077] Therefore, by using the Stirling engine, a start-up operation for a long time is unnecessary before starting the drying operation or at the time of starting the drying operation, so that energy saving that is higher controllability than the heat pump, that is, energy consumption is reduced. This makes it possible to obtain a dryer that can easily reduce energy consumption. In this way, a dryer equipped with a Stirling engine can shorten the time required to start up the dryer, and like a heat pump, it is necessary to wait for the refrigerant to become a uniform gas from the mixture of gas and liquid. Therefore, it is necessary to reduce the time required for starting up again after interrupting the operation once the dryer is running.

Further, the Stirling engine has a wider output control range than the heat pump. Inverter compressors used in heat pumps can control output in the range of 30% to 100%, but in Stirling engines, theoretically, output can be controlled in the range of 0% to 100%. I can do it. For this reason, the excess heat of the circulating air is not increased excessively from the latter stage to the final stage of the drying process, so there is no need to exhaust the circulating air to the outside.

[0079] Further, the vibration system of the heat pump used in the conventional dryer is a complicated vibration system including rotation vibration because the compressor is used for compression and expansion of the refrigerant. On the other hand, a Stirling engine has a simple vibration system compared to a heat pump. That is, in a Stirling engine, only a linear motion of reciprocation of a piston and a displacer is performed.

[0080] Thus, the Stirling engine has a simple vibration system, and therefore can easily absorb vibration. For example, vibration can be easily suppressed by providing a vibration-absorbing member such as a panel having the co-frequency of the displacer vibration as the natural frequency. . In a Stirling engine, vibration can be easily suppressed, so noise due to vibration is less likely to occur.

[0081] By doing so, vibration and noise can be reduced, and usability, that is, use and immediate saving can be reduced without deteriorating the indoor environment in which the dryer is installed. Energy-saving, that is, energy consumption can be effectively reduced, and the washing / drying machine 200 that can easily save energy can be provided.

The washing / drying machine 200 includes a water tank 220 that is disposed so as to cover the rotary drum 230 and accommodates water, and the rotary drum 230 is rotatably supported in the water tank 220. The laundry housed in the interior of the rotary drum 230 can be washed in the rotary drum 230! /.

[0083] By doing in this way, it is possible to dry quickly after washing. In the Stirling engine 410, the high-temperature part and the low-temperature part are not formed separately, for example, connected from the Stirling engine main body by piping, and the compressor, expansion valve, and high-temperature part (condensing part) required for the heat pump are not formed. ), And a simple structure that requires a pipe to circulate the refrigerant connecting the low temperature part (evaporation part). V is easy to generate complex vibration during washing, especially during dehydration. Even in this case, it is possible to provide a highly reliable washing / drying machine 200 that is less likely to break or break down the piping.

The washing / drying machine 200 is configured such that the heat generating head 411 and the heat absorbing head 412 are arranged in the circulation path. By doing so, the washing / drying machine 200 vibrates during washing without the need to provide a path for transferring the heat generated by the heat generating head 411 or the cold air generated by the heat absorbing head 412 to the circulation path, particularly during dehydration where the vibration is increased. Even so, it is possible to provide a highly reliable washing and drying machine 200 with few failures.

[0085] In the washer / dryer 200, a regenerator tube 148 is provided between the heat generating head 411 and the heat absorbing head 412, and the heat generating head 411, the heat absorbing head 412 and the regenerator tube 148 are arranged coaxially. The heat generating head 411, the heat absorbing head 412 and the regenerator tube 148 are arranged in the circulation path!

[0086] By doing so, the circulation path can be shortened to suppress the pressure deficit, and the heat effect of the heat generating head 411 and the heat absorbing head 412 on the regenerator tube 148 can be reduced. It can be reduced by the surrounding air layer.

(Embodiment 1 2)

FIG. 6 is a side sectional view schematically showing a side section of a washing / drying machine as Embodiment 1-2 of the present invention, and FIG. 7 is a section schematically showing a section of the washing / drying machine as viewed from the back. In the figure

[0088] As shown in FIGS. 6 and 7, the washing and drying machine 300 includes a main body 310, a water tank 320 attached to the inside of the main body 310, and a container for storing laundry as an object to be dried. The rotating drum 330 is rotatably supported inside the water tank 320.

An outer door 301 is attached to the upper surface of the main body 310. By opening the outer door 301, the laundry is put into the rotary drum 330 from the laundry inlet 302 provided on the upper surface of the main body 310 through the water tank 320 and the inlet (not shown) provided in the rotary drum 330, or It can be taken out from the rotating drum 330, and the closing force 302 can be closed by closing the outer door 301.

The rotating drum 330 is supported inside the water tank 320 so as to rotate around a shaft portion 331 extending substantially horizontally. In this way, the drum type washing and drying machine 300 has a double structure composed of the water tank 320 and the rotating drum 330. The shaft portion 331 is disposed on each of the left and right sides of the rotating drum 330, and includes a shaft of a drum rotation driving motor 336 for rotating the rotating drum 330, respectively. Note that the drum rotation drive motor may be provided only on one side as long as a desired driving force can be obtained.

[0091] The inner peripheral wall surface of the water tank 320 and the outer peripheral wall surface of the rotating drum 330 form a hot air path part 341 and a humid air path part 342 as circulation paths. An intake port 345 and an exhaust port 346 are provided at the bottom of the water tank 320. Note that the intake port 345 and the exhaust port 346 may be provided in the upper part or the side part. The exhaust port 346 and the intake port 345 are connected to each other as a circulation path outside the water tank 320 via a circulation path part 343. In the circulation path section 343, a heat dehumidifying device 400 including a blower mechanism section 344 and a stirling engine 410 is disposed.

[0092] Inside the main body 310 of the washing and drying machine 300, a hot air path portion 341 and a wet air path portion 342 are arranged on the side surface side of the rotary drum 330. The hot air passage portion 341 and the wet air passage portion 342 communicate with the inside of the water tank 320 through an intake port 345 and an exhaust port 346, respectively. Warm air The passage portion 341 and the wet air passage portion 342 are connected via the circulation passage portion 343 below the water tank 320. In the circulation path part 343 extending substantially linearly, the main body of the heating and dehumidifying device 400 is arranged such that the cooling fin 431 is arranged on the wet air path part 342 side and the heating fin 421 is arranged on the hot air path part 341 side. Is provided. Below the water tank 320, a blower mechanism 344 is disposed inside the wet air passage section 342.

[0093] When the Stirling engine 410 of the heating and dehumidifying device 400 is driven, heat is exchanged so that the gas is heated by the calorie heat fin 421 and the gas is cooled by the cooling fin 431! / Heat exchange.

[0094] By driving the heating and dehumidifying device 400 and the air blowing mechanism 344, the gas heated by the force Q heat fin 421 flows through the hot air path portion 341 as indicated by the two-dot chain line arrow in the figure. Then, it flows into the water tank 320 from the air inlet 345 and blows into the rotating drum 330 disposed inside the water tank 320. The gas comes into contact with the laundry in the rotating drum 330, then flows out of the rotating drum 330 through a small hole, passes through the exhaust port 346 formed in the lower part of the water tank 320, and the wet air passage section 342. Exhausted. The gas exhausted to the wet air passage section 342 has a high humidity due to moisture contained in the laundry in the rotating drum 330. The gas containing moisture flows as indicated by the one-dot chain line arrow in the figure, returns to the cooling fin 431, is cooled by the cooling fin 431, and is dehumidified. The moisture removed from the gas is drained from the main body 310 through the drain pipe (not shown) of the downward force of the cooling fin 431. The dehumidified gas returns to the calo heat fin 421 through the circulation path part 343. The drying process is carried out by repeating this cycle.

The other configurations and effects of the washer / dryer 300 of the embodiment 12 are the same as those of the washer / dryer 200 of the embodiment 11.

[Embodiment 1 3]

FIG. 8 is a perspective view showing another embodiment of the main body of the heating and dehumidifying device provided in the washing and drying machine as Embodiment 13 of the present invention.

[0097] As shown in FIG. 8, the main body of the heating and dehumidifying device 600 includes a Stirling engine 610, a high-temperature side heat exchange unit 620 as a first heat exchange unit, and a low-temperature side heat exchange unit as a second heat exchange unit. 6 and 30. The Stirling engine 610 has a heat generating head 611 and a heat absorbing head 612. To do. The configuration and operation of the Stirling engine 610 are the same as those of the Stirling engine 100 shown in FIG.

The high temperature side heat exchanging unit 620 includes a heating fin 621 connected to the heat generating head 611 as a fin. The heating fin 621 has a disk shape, and the central portion is directly connected to the heating head 611.

[0099] The low temperature side heat exchanging unit 630 includes a cooling unit 632 for cooling the gas, and a heat conduction medium channel 6 for flowing a heat conduction medium for conducting the heat of the heat absorbing head 612 to the cooling unit 632. 33. For example, water is used as the heat conduction medium. The cooling unit 632 may have a plate-like force S in this embodiment, or other forms. In addition, the heat conduction medium flow path 633 may be in the form of a tubular force in this embodiment.

[0100] The heating and dehumidifying device 600 includes this main body, a warm air side path section and a humid air side path section shown in FIG.

[0101] Thus, in the heating and dehumidifying device 600, the high temperature side heat exchanging unit 620 includes the heating head 61.

1 includes heating fins 621 arranged to be in contact with one.

[0102] By doing so, the heat can be efficiently exchanged in the heating fin 621. Further, the heat dehumidifying apparatus 600 can be reduced in size.

[0103] Further, in the heating and dehumidifying device 600, the low temperature side heat exchanging unit 630 includes a cooling unit 632 for cooling the gas and a heat conduction medium for conducting the heat of the heat absorbing head 612 to the cooling unit 632. And a heat conduction medium channel 633 that circulates.

In this manner, for example, the heat generating head 611, the heating fin 621, and the cooling unit 63 are used.

It is easy to reduce the thermal effect exerted on each other by separating the distance on the air path with 2. Also

Optimize the position and shape of the cooling part 632, such as the arrangement of the cooling part 632 in the surplus space, according to the shape of the wet air passage part 242 (Fig. 5) and the overall part arrangement of the washer / dryer 200. Becomes easier.

In addition, in the washer / dryer 200, the heat generating head 611 is disposed in the circulation path and constitutes the high temperature side heat exchanging unit 620.

In this way, the heat transfer path from the heat generating head 611 to the high temperature side heat exchanging unit 620 becomes unnecessary, the number of parts of the heating dehumidifying device 600 is reduced, and the manufacturing of the heating dehumidifying device 600 is reduced. A highly reliable V-type washing and drying machine 200 that can simplify the process and prevent damage to pipes due to vibration in the heat transfer path from the heating head 611 to the high-temperature side heat exchange section 620. Can be provided.

[0107] Other configurations and effects of the washer-dryer 200 of Embodiment 13 are the same as those of Embodiment 11.

[Embodiment 1 4]

[0109] As shown in Fig. 9, the heating and dehumidifying device 700 includes a Stirling engine 710, a high-temperature side heat exchange unit 720 as a first heat exchange unit, and a low-temperature side heat exchange unit 730 as a second heat exchange unit. And. The Stirling engine 710 has a heat generating head 711 and a heat absorbing head 712. The configuration and operation of Stirling engine 710 are the same as Stirling engine 100 shown in FIG.

[0110] The high temperature side heat exchanging unit 720 includes a heating unit 722 for heating a gas, and a heat conduction medium channel 7 for circulating a heat conduction medium for conducting heat from the heating head 711 to the heating unit 722. And 23. For example, water is used as the heat conduction medium. The heating unit 722 has a plate shape in this embodiment, but may have other forms. Further, the heat transfer medium flow path 723 may have a force S that is tubular in this embodiment, or other forms.

[0111] The low temperature side heat exchanging section 730 includes cooling fins 731 connected to the heat absorbing head 712 as fins. The cooling fin 731 has a disk shape, and the central portion is directly connected to the heat absorbing head 712.

[0112] The heating and dehumidifying device 700 includes this main body, and a warm air side path section and a humid air side path section shown in FIG.

As described above, in the heating and dehumidifying device 700, the high temperature side heat exchanging unit 720 includes the heating unit 722 for heating the gas and the heat transfer for conducting the heat of the heating head 711 to the heating unit 722. A heat transfer medium flow path 723 through which the medium flows.

[0114] By doing so, for example, it becomes easy to reduce the influence of heat on the air path between the heating unit 722, the heat absorbing head 712, and the cooling fin 731, by separating the distance on the air path. Also Optimize the position and shape of the heating part 722, such as the arrangement of the heating part 722 in the surplus space, according to the shape of the hot air path part 241 (Fig. 5) and the overall parts arrangement of the washer / dryer 200, etc. Easy to do.

[0115] In the washer / dryer 200, the heat absorbing head 712 is disposed in the circulation path and constitutes the low temperature side heat exchanging section 730.

[0116] This eliminates the need for a cold air transmission path from the heat absorbing head 712 to the low temperature side heat exchanging section 730, reduces the number of parts of the heating dehumidifier 700, and facilitates the production of the heating dehumidifier 700. It is possible to provide a highly reliable washing and drying machine 200 that can prevent damage to pipes due to vibration in the cold air transmission path from the heat absorbing head 712 to the low temperature side heat exchanging unit 730. it can.

[0117] Further, in this way, in the heat dehumidifying apparatus 700, the low temperature side heat exchanging unit 730 includes the cooling fins 731 arranged so as to be in contact with the heat absorbing head 712.

[0118] By doing so, the heat can be efficiently exchanged in the cooling fins 731. In addition, the heat dehumidifier 700 can be downsized.

[0119] Other configurations and effects of the washer / dryer 200 of the embodiment 14 are the same as those of the embodiment 11 of the present invention.

[0120] (Embodiment 2-1)

Hereinafter, Embodiment 2-1 of the present invention will be described with reference to FIG. 10 and FIG. FIG. 10 is a cross-sectional view showing the configuration of the water supply / drainage path of the drum type laundry dryer according to Embodiment 21 of the present invention, and FIG. 11 shows the drying ventilation path of the drum type laundry dryer according to Embodiment 21 of the present invention. It is sectional drawing which shows the structure of this.

[0121] As shown in Fig. 10, an entrance la for loading and unloading laundry is formed on the front surface of the substantially rectangular parallelepiped body 1, and a door 2 for opening and closing the entrance la is provided by a hinge mechanism. It is provided so that it can rotate. Inside the main body 1, a bottomed cylindrical water tank 3 having an opening 3 a facing the inlet la at one end is slanted so that the opening 3 a side is higher with respect to the rear surface. The opening 3a of the water tank 3 and the inlet la of the main body 1 are watertightly connected by a packing 4. The water tank 3 is supported by a support device such as a damper (not shown) so that it can be swung freely. [0122] In the water tank 3, a rotary tank 5 for storing laundry is rotatably mounted. The rotating tank 5 has a bottomed cylindrical shape having an opening 5a opposite to the opening 3a at one end in the rotation axis direction, and is inclined so that the opening 5a side is higher than the bottom surface (rear surface). is doing. A fluid balancer 6 is provided on the periphery of the opening of the rotary tank 5, and a plurality of holes are provided in the peripheral wall of the rotary tank 5. In the state where the door 2 is rotated to open the input port la, the laundry is put into the rotary tub 5 and the laundry is taken out from the rotary tub 5 through the input port la, the opening 3a, and the opening 5a. Done.

[0123] A rotating shaft 5b is fixed to the bottom surface (rear surface) of the rotating tub 5, and is rotatably supported by the water tub 3 via a bearing 5c so that the rotating shaft is inclined. A drum pulley 5d is attached to the end of the rotating shaft 5b opposite to the side on which the rotating tub is attached.

[0124] In the upper part of the back of the main unit 1, there is a stepped portion with the top surface of the main unit 1 partially lowered, and the water supply port 7 for introducing water from the water supply into the main unit 1 is arranged on the stepped portion. Yes. A water supply valve (not shown) is arranged on the downstream side of the water supply port 7, and the water supply valve is opened and closed in accordance with instructions from a control device (not shown) that controls the operation of each part of the washing machine. Be controlled. When the water supply valve is opened by an instruction from the control device, water from the water channel is introduced into the main body 1 through the water supply port 7. The water that has passed through the water supply port 7 is supplied into the detergent case 9 through the water supply channel 8 and mixed with the detergent, and then supplied into the water tank 3 through the water supply pipe 10.

[0125] Further, a drain pipe 11 that constitutes a discharge path for the water supplied into the water tank 3 to the outside of the main body 1 is connected to the lower rear side of the water tank 3. Foreign matter such as lint is removed from the water discharged from the water tank 3 to the drain pipe 11 by the drain filter 12a disposed in the filter device 12. The filter device 12 is provided with an air trap 12b, and one end of a pressure guiding tube 13 communicating with the inside of the air trap 12b is connected. A water level sensor 14 is connected to the other end of the pressure guiding tube 13, and when it is easy to wash, the water level in the water tank 3 is detected by measuring the air pressure in the air trap 12b with the water level sensor 14. The The water from which foreign matter has been removed by the filter device 12 flows into the drainage channel 15. A drain valve 16 is arranged on the downstream side of the drainage channel 15. The drain valve 16 is opened and closed in accordance with instructions from a control device (not shown) that controls the operation of each part of the washing machine, and drainage from the inside of the main body 1 is performed. Be controlled. In response to instructions from the control unit When the drain valve 16 is further opened, the water in the drain channel 15 is drained out of the main body 1 through the drain hose 17. The drainage channel 15 and the drainage hose 17 are part of the drainage channel.

As shown in FIG. 11, an installation table 18 is provided at the lower part of the water tank, and a motor 19 capable of controlling the rotational speed for rotating the rotary tank 5 is arranged on the installation table 18. ing. A motor shaft 19a is attached to the motor 19, and a motor pulley 20 is provided on the opposite side of the motor shaft 19a from which the motor 19 is attached. The motor pulley 20 and the rotary tank pulley 5d are wound around the belt 21 so that the power of the motor pulley 20 can be transmitted to the rotary tank pulley 5d.

[0127] A clutch mechanism 22 is passed through the motor shaft 19a, and the motor shaft 19a can be switched between a state in which the rotational driving force of the motor shaft 19a is transmitted to a transmission mechanism portion 23 provided therebelow or a state in which it is not transmitted. It is configured. The rotational driving force transmitted to the transmission mechanism unit 23 is supplied to the heat exchange unit 24 and used as power for the heat exchange unit 24. More detailed configurations and operations of the clutch mechanism 22, the transmission mechanism unit 23, and the heat exchange unit 24 will be described later.

[0128] A ventilation path (circulation duct) 25, which is an example of a circulation duct through which air for drying the washing material put in the rotary tank 5 circulates from the rear rear side to the lower part and the front front side of the water tank, is provided. Is provided. In the ventilation path 25, a blower 26 and a heat exchange unit 24 that are air flow sources of the ventilation path 25 are arranged in the path. During the drying operation, the air in the water tank 3 is discharged to the ventilation path 25 through the exhaust port 25a. The air flowing into the ventilation path 25 is sent to the heat exchanging unit 24 by a blower 26 which is an example of a fan, cooled and dehumidified by a heat absorbing head 38a, which will be described later, and then heated by a heat generating head 38b to be supplied to an air supply port. From 25b, it is sent to tank 3 again. A part of the ventilation path 25 may be provided along the peripheral edge of the back surface of the water tank 3.

Next, the configuration of the clutch mechanism 22, the transmission mechanism unit 23, and the heat exchange unit 24 will be described with reference to FIGS. FIG. 12 is an enlarged view of the main part of FIG. 11, FIG. 13 is an exploded perspective view of the clutch mechanism 22, and FIG. 14 is a view of FIG.

As shown in FIG. 12, the clutch mechanism 22 includes an interlocking shaft 27, a clutch piece 28, a coil spring 29, and a solenoid 30. The interlocking shaft 27 is threaded so as to be rotatable with respect to the motor shaft 19a. The interlocking shaft 27 is configured to have a smaller diameter closer to the motor 19 and a larger diameter farther away. The As shown in FIG. 13, the small-diameter portion 27a, which is the small-diameter portion of the interlocking shaft 27, is formed in a cross-shaped cross section so that a portion protrudes in the radial direction every 90 °. The large-diameter portion 27b, which is the large-diameter portion of the interlocking shaft 27, has a gear-like periphery, and is connected to a first transmission gear 31 described later so that power can be transmitted. A connecting part 19b formed integrally with the motor shaft 19a is formed adjacent to the small diameter part 27a of the interlocking shaft 27 and closer to the motor 19 than the small diameter part 27a of the interlocking shaft 27. As shown in FIG. 13, the connecting portion 19b is formed in a cross-shaped cross section so that a portion protrudes in the radial direction every 90 °, and has the same shape as the small-diameter portion 27a of the interlocking shaft 27. Yes. The clutch piece 28 is made of a magnetic material. As shown in FIG. 13, the outer peripheral side is formed in a circular shape, and the inner peripheral side is formed so that a part thereof is depressed in the radial direction every 90 °. The outer periphery of the small-diameter portion 27a of the interlocking shaft 27 and the outer periphery of the connecting portion 19b are fitted to the inner peripheral side. A coil panel 29 is compressed and disposed between the large-diameter portion 27b of the interlocking shaft 27 and the clutch piece 28, and urges the clutch piece 28 to be engaged only with the connecting portion 19b. On the outer peripheral side of the clutch piece 28, as shown in FIG. 12, a solenoid 30 for generating a magnetic force and generating a repulsive force on the clutch piece 28 is disposed. The solenoid 30 is driven to move the clutch piece 28 against the urging force of the coil panel 29, and as shown in FIG. 15 to be described later, the clutch piece 28 is fitted to the connecting portion 19b and the small diameter portion 27a. The urging force is adjusted so that the rotational driving force of the motor 19 is transmitted to the transmission mechanism 23.

As shown in FIG. 12, the transmission mechanism unit 23 includes a first transmission gear 31 and a second transmission gear 32. As shown in FIG. 14, the first transmission gear 31 is provided below the large-diameter portion 27b of the interlocking shaft 27, and the outer peripheral gear and the gear of the large-diameter portion 27b of the interlocking shaft 27 are fitted together. Therefore, the rotational driving force of the interlocking shaft 27 is transmitted to the second transmission gear 32 disposed below the interlocking shaft 27. As shown in FIG. 13, the second transmission gear 32 is formed so that one side in the rotation axis direction is a small diameter portion 32a that is a small diameter gear and the other side is a large diameter portion 32b that is a large diameter gear. Yes. In the second transmission gear 32, the small-diameter portion 32a is engaged with the first transmission gear 31 and the large-diameter portion 32b is engaged with a shaft gear 33 which will be described later, and the rotational driving force of the first transmission gear 31 is used as the shaft gear 33. Communicate to The clutch mechanism 22 and the transmission mechanism unit 23 are examples of the transmission unit. [0132] In the present embodiment, the heat exchanging unit 24 uses a parallel two-piston Stirling refrigerator. As shown in Fig. 12, shaft gear 33, crankshaft 34, heat absorption side crank 35a, heat generation side crank 35b, heat absorption side piston 36a, heat generation side piston 36b, low temperature chamber 37a, high temperature chamber 37b, heat absorption head 38a, heat generation It comprises a head 38b and a regenerator 39. The shaft gear 33 is disposed below the large-diameter portion 32b of the second transmission gear 32, and is engaged with the gear of the large-diameter portion 32b of the second transmission gear 32. The shaft gear 33 has a crankshaft 34 attached to the body extending toward the front side of the product. The crankshaft 34 is rotatably supported at two places on the installation base 18, and a heat absorbing side crank connecting portion 34a and a heat generating side crank connecting portion 34b are provided between the portions that are supported by the shaft. In FIG. 12, the heat absorption side crank connection portion 34a is bent so as to protrude upward, and the heat generation side crank connection portion 34b is bent so as to protrude toward the front side, so that the shaft gear 33 is as shown in FIG. By turning counterclockwise (counterclockwise) as viewed from the rear of the main unit 1, the heat generating side crank connecting part 34b is rotated by 90 ° with respect to the heat absorbing side crank connecting part 34a. The heat absorbing head 38a described later operates so as to cool the air in the ventilation path 25, and the heat generating head 38b operates to heat the air in the ventilation path 25.

[0133] The heat absorption side crank connection portion 34a and the heat generation side crank connection portion 34b are connected to one end of the heat absorption side crank 35a and the heat generation side crank 35b. The heat absorption side crank 35a and the heat generation side crank 35b are connected to the other end of the heat absorption side piston 36a and the heat generation side piston 36b, respectively. Below the heat absorption side piston 36a and the heat generation side piston 36b, there are provided a low temperature chamber 37a and a high temperature chamber 37b in which gas such as hydrogen and helium is sealed with the installation base 18 as an outline, respectively. 36a and the inner surface of the low temperature chamber 37a and the heat generating side piston 36b and the inner surface of the high temperature chamber 37b are configured to be airtight and slidable. The tip portions protruding into the ventilation path 25 below the low greenhouse 37a and the high temperature chamber 37b function as a heat absorption head 38a that cools the air in the ventilation path 25 and a heat generation head 38b that heats the air in the ventilation path 25. The heat absorbing head 38a and the heat generating head 38b are not necessarily projected into the ventilation path 25, but are preferably projected into the ventilation path 25 in order to improve heat exchange efficiency. This cooling and heating function will be described later. In addition, the low temperature room 37a and the high temperature room 37b have paths that allow the rooms to communicate with each other. Has been. The regenerator 39 has an effect of storing heat from the high-temperature gas passing through the periphery or supplying the stored heat to the low-temperature gas. The heat absorption head 38a and the heat generation head 38b are arranged so that their arrangement directions coincide with the projection axis of the rotation axis of the rotary tank 5 onto the horizontal plane, and vibration that vibrates integrally with the water tank 3 in the main body 1 during operation. By pushing down the body's center of gravity downward, it is easier to reduce vibration. As a result, even when the rotating tub 5 is arranged at a high position, the laundry can be easily taken out while contributing to noise reduction. The mounting table 18 is an example of a housing.

[0134] Next, the operation of the washing / drying machine will be described. In the washing / drying machine with the configuration, the user turns on the power, puts the laundry into the rotary tub 5 from the insertion port, and puts the detergent into the detergent case 9, and then the start switch of the operation panel (not shown) When the operation is started by pressing, the control unit supplies water to the water tank 3 through the water supply port 7, the water supply channel 8, the detergent case 9 and the water supply pipe 10. When the water level sensor 14 detects that the water level in the water tank 3 has reached a predetermined water level, the control unit stops water supply to the water tank 3 and drives the motor 19 to rotate the rotary tank 5 at a low speed. Washing process.

[0135] When the washing process is completed, the water in the tank 3 is drained out of the machine through the drain pipe 11, filter device 12, drain channel 15, drain valve 16 and drain hose 17, and then the rotary tank 5 is put into high speed. Rotate to dehydrate laundry water contained in the laundry. When the dehydration process is completed, a rinsing process for rotating the rotating tank 5 at a low speed is started after water supply to the water tank 3 to a predetermined water level again. When the rinsing process is completed, the dewatering process is performed after the washing water in the water tank 3 is drained. After the rinsing process and the dehydrating process are repeated a plurality of times, the process proceeds to the drying process.

Next, the operation of the main part of the drying process of Embodiment 2-1 of the present invention will be described using FIG. 15 to FIG. Fig. 15 is an enlarged view of the main part in a state where the clutch mechanism 22 is switched so as to transmit the rotational driving force to the heat exchanging unit 24, and Fig. 16 is a state in which the crankshaft 34 is rotated 90 ° from the state of Fig. 15. Fig. 17 is an enlarged view of the main part of the crankshaft 34 rotated 180 ° from the state of Fig. 15, and Fig. 18 is a crankshaft 34 rotated 270 ° from the state of Fig. 15. It is a principal part enlarged view of a state.

[0137] When the drying process is started, the blower 26 is driven to blow air in the ventilation path 25, and the solenoid 30 is driven to move the clutch piece 28 to the connecting portion 19b and the interlocking shaft 27. As a result, the rotational driving force of the motor 19 can be transmitted to the interlocking shaft 27. In this state, when the motor 19 is rotated clockwise as shown in FIG. 14, the rotating tub 5 is rotated clockwise as viewed from the rear, and the interlocking shaft 27 is also rotated in the same arrow a direction. The first transmission gear 31 is rotated counterclockwise in the direction of arrow b. The rotation driving force transmitted to the first transmission gear 31 is transmitted to the second rotation gear 32 fitted to the first transmission gear 31, and the second transmission gear 32 is rotated in the direction of the arrow c. The second transmission gear 32 that rotates in the direction of the arrow c rotates the shaft gear 33 in the direction of the arrow d to drive the heat exchange unit 24.

In the state shown in FIG. 15, while the shaft gear 33 is driven in the direction of the arrow d to reach the state shown in FIG. 16, the heat absorption side crank connection portion 34a and the heat generation side crank connection portion 34b are connected to the heat absorption side crank 35a. Then, the heat generating side crank 35b is driven downward and the gas in the low temperature chamber 37a and the high temperature chamber 37b is compressed by the heat absorbing side piston 36a and the heat generating side piston 36b having a phase difference of 90 degrees. At this time, the compressibility of the gas in the high temperature chamber 37b is much larger than that in the low temperature chamber 37a. Since the pressure and temperature of the gas in the high temperature chamber 37b increase, the temperature of the heating head 38b increases and the high pressure in the high temperature chamber 37b increases. Then, the gas whose temperature has increased is blown into the low temperature chamber 37a through the regenerator 39. When the gas whose temperature has been increased due to the high pressure in the high temperature chamber 37b passes through the regenerator 39, the heat quantity of this gas is stored in the regenerator 39, and the cooled gas is blown into the low temperature chamber 37a after the heat quantity is removed. To lower the temperature of the low temperature chamber 37a.

[0139] While the rotation of the shaft gear 33 advances and the state of FIG. 16 shifts to the state of FIG. 17, the endothermic crank connecting portion 34a pushes the endothermic crank 35a downward, and the heat generating side The crank connecting part 34b drives the heat generating side crank 35b to lift upward, compresses the gas in the low temperature chamber 37a by the heat absorbing side piston 36a, and expands the gas in the high temperature chamber 37b by the heat generating side piston 36b. The gas in chamber 37a moves rapidly through regenerator 39 to high greenhouse 37b. At this time, the gas moving to the high temperature chamber 37b is heated by the amount of heat stored in the regenerator 39, the temperature rises, and the temperature in the high temperature chamber 37b rises.

[0140] While the shaft gear 33 is further rotated to shift from the state shown in Fig. 17 to the state shown in Fig. 18, the heat absorption side crank connection portion 34a and the heat generation side crank connection portion 34b are connected to the heat absorption side crank 35a. And the heat generating side crank 35b is driven upward to lift the heat absorbing side piston. The gas in the low temperature chamber 37a and the high temperature chamber 37b is expanded by 36a and the heat generating side piston 36b. At this time, the expansion rate of the gas in the low temperature chamber 37a is much larger than that in the high temperature chamber 37b, and the pressure and temperature of the gas in the low temperature chamber 37a decrease, so the temperature of the endothermic head 38a decreases.

[0141] While the shaft gear 33 is further rotated to shift from the state shown in Fig. 18 to the state shown in Fig. 15, the endothermic crank connecting portion 34a generates heat in the direction of lifting the endothermic crank 35a upward. The side crank connecting portion 34b drives the heat generating side crank 35b to push downward, expands the gas in the low temperature chamber 37a by the heat absorption side piston 36a, and compresses the gas in the high temperature chamber 37b by the heat generation side piston 36b. The gas in the high greenhouse 37b moves rapidly through the regenerator 39 to the low greenhouse 37a. At this time, the amount of heat of the gas moving to the low temperature chamber 37a is stored in the regenerator 39, and the gas whose temperature has decreased is blown into the low temperature chamber 37a. As the shaft gear 33 rotates in this manner, the heat absorbing head 38a cools and the heat generating head 38b generates heat, and the temperature decreases and rises according to the rotational speed of the shaft gear 33, respectively.

[0142] In the drying process, the air discharged from the water tank 3 into the ventilation path 25 through the exhaust port 25a is sent to the heat absorbing head 38a through the blower 26. The air sent to the heat absorbing head 38a is cooled and dehumidified by the heat absorbing head 38a, and then sent to the heat generating head 38b. The air sent to the heat generating head 38b is heated by the heat generating head 38b and blown into the water tub 3 to evaporate the moisture in the laundry in the rotating tub and advance the drying. Thereafter, the end of drying is detected by detection of a humidity sensor or a temperature sensor (not shown) and the operation is terminated. A drainage hole (not shown) is provided at the bottom of the ventilation path 25 below the heat absorption head 38a. When water (drain water) is condensed on the bottom heat absorption head 38a, the ventilation path 25 and the drainage hose 17 are discharged from the drainage hole. It is drained by a drain hose that connects the two.

[0143] As described above, according to Embodiment 2-1 of the present invention, by providing the clutch mechanism 22 on the motor shaft 19a of the motor 19 that rotates the rotating tub 5, the rotational driving force of the motor 19 is exchanged with heat. Since the heat exchange unit 24 can be operated by transmitting it to the exchange unit 24, it is possible to provide a high energy-saving and / or washing machine that does not require a separate motor for operating the reverse Stirling cycle. In addition, since the ventilation path 25 is provided in the lower part of the main body 1, the arrangement height of the water tank 3 which does not require a large space on the main body 1 and the top of the water tank 3 can be increased. The washing machine can be easily taken out. Further, since the center of gravity is arranged below the water tank 3 along its center line, it can also act as a weight for preventing vibrations, and can increase the noise. In addition, since a part of the ventilation path 25 is disposed below the heat exchange unit 24 and above the drainage channel 15 or the drainage hose 17, that is, between the two, drainage of drain water cooled and dehumidified by the heat exchange unit The route can be shortened and drained quickly.

[Embodiment 2—2]

Hereinafter, Embodiment 2-2 of the present invention will be described with reference to FIGS. FIG. 19 is a cross-sectional view of the drum type washing and drying machine according to Embodiment 2-2 of the present invention, FIG. 20 is an enlarged view of the main part of FIG. 19, FIG. 21 is a cross-sectional view of FIG. FIG. 4 is an exploded perspective view of a configuration around a motor shaft 40b. In the embodiment 2-2, the same components as those in the embodiment 2-1 are denoted by the same reference numerals and description thereof is omitted.

In Embodiment 2-2, a drive unit 40 and a ventilation path 41, which are examples of a motor, are provided on the back surface of the water tank 3. As shown in FIG. 20, the drive unit 40 is covered with a motor cover 40a, and a motor shaft 40b, one end of which is connected to the center of the back surface of the rotary tank 5, is freely rotatable by a bearing 40c. It is supported by. A rotor 40d is attached to the other end of the motor shaft 40b, and has an inner rotor type direct drive system configuration in which a rotational driving force is applied by a stator 40e provided on the outer peripheral side thereof. Further, the motor shaft 40b is provided with a connecting portion 40f in which a part of the motor shaft 40b has a large diameter. As shown in FIG. 22, the connecting portion 40f is formed in a cross-shaped cross section so that a part protrudes in the radial direction every 90 °.

[0146] Further, a ventilation path 41 is provided from the back surface to the peripheral surface of the water tank 3. The ventilation path 41 provided on the rear side is arranged so as to surround the outer periphery of the drive unit 40 in the clockwise direction from above so as to substantially follow the peripheral edge of the rear surface of the aquarium 3. It is provided so that the three circumferential surfaces of the water tank extend forward. As shown in FIG. 21, the ventilation path 41 is formed between an exhaust port 41a that is a communication port with the inside of the water tank 3, a casing 4 lb that is an outline of the ventilation path 41, and a rear surface of the water tank 3 and the casing 41b. Water tank rear surface path 41c, air blower 41d which is the air flow source of the air flow path 41, and water tank formed between the water tank 3 circumferential surface and the casing 4 lb And a circumferential path 41 e. A heat absorbing head 54a and a heat generating head 54b of a heat exchanging section 48, which will be described later, protrude from the water tank rear path 41c, and the air in the water tank rear path 41c is cooled and dehumidified and heated by the heat absorbing head 54a and the heat generating head 54b. To be dried. Although not shown, the air supply port to the water tank 3 in the water tank peripheral surface path 41e is arranged so that the air that has passed through the ventilation path 41 is blown into the rotation tank 5 from the opening 5a of the rotation tank 5. Yes. The blower 41d is an example of the fan, and the water tank rear surface path 41c and the water tank peripheral surface path 41e are examples of the circulation duct.

[0147] On the outer periphery of the motor shaft 40b, as shown in Fig. 20, an interlocking shaft 42 is rotatably disposed adjacent to the connecting portion 40f. As shown in FIG. 22, the interlocking shaft 42 is configured such that a portion adjacent to the connecting portion 40f has a small diameter and a portion apart from the connecting portion 40f has a large diameter. As shown in FIG. 22, the small-diameter portion 42a, which is the small-diameter portion of the interlocking shaft 42, is formed in a cross-shaped cross section so that a portion protrudes in the radial direction every 90 °, and has the same shape as the connecting portion 40f. Is formed. On the other hand, the large-diameter portion 42b, which is the large-diameter portion of the interlocking shaft 42, is formed in a gear shape, and this gear is connected to a transmission gear 46, which will be described later, so as to transmit the rotational driving force. Yes.

[0148] As shown in FIG. 20, a clutch piece 43 is provided on the outer periphery of the connecting portion 40f. The clutch piece 43 is made of a magnetic material, and as shown in FIG. 22, the outer peripheral side is formed in a circular shape, and the inner peripheral side is partially recessed in the radial direction every 90 °. The outer periphery of the small-diameter part 42a of the interlocking shaft 42 and the connecting part 40f is formed on the inner periphery. A coil spring 44 is compressively disposed between the large-diameter portion 42b of the interlocking shaft 42 and the clutch piece 43, and urges the clutch piece 43 to be engaged only with the connecting portion 40f. On the outer peripheral side of the clutch piece 43, as shown in FIG. 20, a solenoid 45 that generates a magnetic force to generate a repulsive force on the clutch piece 43 is disposed. The solenoid 45 is driven to move the clutch piece 43 against the urging force of the coil spring 44, and the clutch piece 43 is engaged with both the connecting portion 40f and the interlocking shaft 42 to rotate the driving force of the motor shaft 40b. The urging force is adjusted so as to be transmitted to a transmission gear 46 described later.

[0149] A transmission gear 46 is arranged below the large-diameter portion 42b of the interlocking shaft 42 as shown in FIG. The transmission gear 46 is connected to the gear of the large-diameter portion 42b of the interlocking shaft 42 above the transmission gear 46, and is also connected to the gear portion of the crank gear 47 provided therebelow. Crank gear 47 A small-diameter gear 47a (broken line in FIG. 22), a disk-shaped large-diameter 47b, and a cylindrical shape that protrudes vertically from the surface of the large-diameter 47b opposite to the surface on which the gear 47a is provided. The crankpin is composed of 47c. A heat exchanging section 48 is provided below the crank gear 47 as shown in FIG. The interlocking shaft 42, the clutch piece 43, the coil spring 44, the solenoid 45, the transmission gear 46, and the crank gear 47 are examples of the transmission unit.

Here, the heat exchanging unit 48 will be described with reference to FIG. FIG. 23 is a CC cross-sectional view of FIG.

[0151] The heat exchanging section 48 uses a V-type two-piston Stirling refrigerator in the present embodiment.

As shown in FIG. 23, the outer shell is configured integrally with the motor cover 40a, and the heat absorption side crank 49a, the heat generation side crank 49b, the heat absorption side cross head 50a, the heat generation side cross head 50b, the heat absorption side piston pin 51a, the heat generation side. Side piston pin 51b, heat absorption side piston 52a, heat generation side piston 52b, low temperature chamber 53a, high temperature chamber 53b, heat absorption head 54a, heat generation head 54b, low temperature chamber air inlet / outlet 55a, high temperature chamber air inlet / outlet 55b, low temperature air passage 56a, A hot air passage 56b and a regenerator 57 are provided.

[0152] One end of each of the heat absorption side crank 49a and the heat generation side crank 49b is rotatably connected to the crank pin 47c. On the other hand, the other ends of the heat absorption side crank 49a and the heat generation side crank 49b are rotatably connected to the heat absorption side cross head 50a and the heat generation side cross head 50b, and the rotational driving force of the drive unit 40 transmitted from the crank pin 47c is generated. introduce. The heat absorption side crosshead 50a and the heat generation side crosshead 50b are swingably fitted to the inner surface of the cylindrical motor cover 40a, and are transmitted from the heat absorption side crank 49a and the heat generation side crank 49b. The generated driving force is transmitted in the axial direction of each piston pin to the heat absorption side piston pin 5 la and the heat generation side piston pin 5 lb connected to the heat absorption side cross head 50a and the heat generation side cross head 50b. The heat absorption side piston pin 51a and the heat generation side piston pin 51b are arranged so that the axial directions thereof are substantially perpendicular when viewed from the back side of the water tank 3.

[0153] Further, one end of the heat absorption side piston pin 51a and the heat generation side piston pin 51b is connected to the heat absorption side cross head 50a and the heat generation side cross head 50b, and the other end is connected to the heat absorption side piston 52a and the heat generation side piston 52b. It is connected. The heat absorption side piston 52a and the heat generation side piston 52b are slidable on the inner peripheral surface of the motor cover 40a formed in a cylindrical shape, Each sliding surface between the heat side piston 52a and the heat generation side piston 52b and the inner peripheral surface of the motor cover 40a is fitted so as to be hermetically sealed. On the side of the heat absorption side piston 52a and the heat generation side piston 52b opposite to the surface where the heat absorption side piston pin 51a and the heat generation side piston pin 51b are attached, there are a low temperature chamber 53a and a high temperature chamber 53b. The tip end side is closed by the heat absorbing head 54a and the heat generating head 54b.

[0154] The low greenhouse 53a and the high temperature chamber 53b have a low temperature room air inlet / outlet 55a and a high temperature room air inlet / outlet 55b that open toward the rear side of the main body, and the low temperature room air inlet / outlet 55a and the high temperature room air inlet / outlet respectively. It communicates with the low temperature air passage 56a and the high temperature air passage 56b through 55b. A regenerator 57 is connected to the path between the low temperature air path 56a and the high temperature air path 56b. Air in the low greenhouse 53a is sent to the high temperature chamber 53b through the low temperature chamber air inlet / outlet 55a, the low temperature air passage 56a, the regenerator 57, the high temperature air passage 56b, and the high greenhouse air inlet / outlet 55b by the operation of the heat absorption side piston 52a. On the contrary, the air in the high temperature chamber 53b is moved into the low temperature chamber 53a through the operation of the heat generating piston 52b through the high temperature chamber air inlet / outlet 55b, the high temperature air passage 56b, the regenerator 57, the low temperature air passage 56a, and the low temperature chamber air inlet / outlet 55a. Sent to. At this time, the regenerator 57 absorbs the heat of the air flowing from the high temperature air passage 56b and discharges the heat to the air flowing from the low temperature air passage 56a, so that the air in the low temperature chamber 53a is low temperature and the air in the high temperature chamber 53b. Acts to maintain a high temperature.

Next, the operation of the main part of the drying process of Embodiment 2-2 of the present invention will be described with reference to FIG. 21, FIG. 23 to FIG. Fig. 24 is an enlarged view of the main part when the crank gear 47 is rotated 90 ° from the state of Fig. 23, and Fig. 25 is an enlarged view of the main part when the crank gear 47 is rotated 180 ° from the state of Fig. 23. FIG. 26 and FIG. 26 are enlarged views of essential parts in a state where the crank gear 47 is rotated 270 ° from the state of FIG.

[0156] When the drying process is started, the blower 41d is driven to blow air in the ventilation path 41, and the solenoid 45 is driven to engage the clutch piece 43 with the connecting portion 40f and the interlocking shaft 42. Thus, the rotational driving force of the drive unit 40 can be transmitted to the interlocking shaft 42. In this state, when the drive unit 40 is rotated in the clockwise direction e as shown in FIG. 21, the rotating tub 5 is rotated clockwise around the motor shaft 40b when viewed from the rear, and The interlocking shaft 42 also rotates in the same arrow e direction to rotate the transmission gear 46 in the counterclockwise arrow f direction. Transmitted to transmission gear 46 The rotation driving force rotates the crank gear 47 fitted thereto in the direction of the arrow g to drive the heat exchanging portion 48.

In the state of FIG. 23, while the crank gear 47 is driven in the direction of the arrow g in FIG. 21 and enters the state of FIG. 24, the heat absorption side crank 49a moves the heat absorption side crosshead 50a upward. The heat generation side crank 49b drives the heat generation side crosshead 50b to push downward, expands the gas in the low temperature chamber 53a by the heat absorption side piston 52a, and expands the gas in the high temperature chamber 53b by the heat generation side piston 52b. In order to compress, the gas in the high temperature chamber 53b rapidly moves to the low temperature chamber 53a through the regenerator 57. At this time, the amount of heat of the gas moving to the low temperature chamber 53a is stored in the regenerator 57, and the gas whose temperature has decreased is blown into the low temperature chamber 53a.

[0158] While the rotation of the crank gear 47 advances and the transition from the state of Fig. 24 to the state of Fig. 25 is made, the heat absorption side crank 49a and the heat generation side crank 49b are connected to the heat absorption side cross head 50a and the heat generation side cross. The head 50b is driven upward and the gas in the low temperature chamber 53a and the high temperature chamber 53b is expanded by the heat absorption side piston 52a and the heat generation side piston 52b. At this time, the expansion rate of the gas in the low temperature chamber 53a is much larger than that in the high temperature chamber 53b, and the pressure and temperature of the gas in the low temperature chamber 53a decrease, so the temperature of the endothermic head 54a decreases.

[0159] While the rotation of the crank gear 47 advances and the state of FIG. 25 shifts to the state of FIG. 26, the heat absorption side crank 49a pushes the heat absorption side crosshead 50a downward, and the heat generation side crank 49b drives the heat generating side cross head 50b to lift upward, compresses the gas in the low temperature chamber 53a by the heat absorption side piston 52a, and expands the gas in the high temperature chamber 53b by the heat generation side piston 52b. The gas rapidly moves through the regenerator 57 to the high temperature chamber 53b. At this time, the gas moving to the high temperature chamber 53b is heated by the amount of heat stored in the regenerator 57, the temperature rises, and the temperature in the high temperature chamber 53b rises.

[0160] While the rotation of the crank gear 47 advances and the state of FIG. 26 shifts to the state of FIG. 23, the heat absorption side crank 49a and the heat generation side crank 49b are connected to the heat absorption side cross head 50a and the heat generation side cross. The head 50b is driven downward and the gas in the low temperature chamber 53a and the high temperature chamber 53b is compressed by the heat absorption side piston 52a and the heat generation side piston 52b. At this time, the compressibility of the gas in the high temperature chamber 53b is much higher than that in the low temperature chamber 53a. Since the pressure and temperature of the gas in the chamber 53b rise, the temperature of the heat generating head 54b rises, and the gas whose temperature has increased at a high pressure in the high temperature chamber 53b is blown into the low temperature chamber 53a through the regenerator 57. When the gas whose temperature has been increased due to the high pressure in the high temperature chamber 53b passes through the regenerator 57, the heat quantity of this gas is stored in the regenerator 57, and the cooled gas is blown into the low temperature chamber 53a. To lower the temperature of the cold chamber 53a. As the crank gear 47 rotates in this manner, the heat absorbing head 54a cools and the heat generating head 54b generates heat, and the temperature decreases and increases according to the rotational speed of the crank gear 47, respectively.

[0161] In the drying step, the air discharged from the water tank 3 into the ventilation path 41 through the exhaust port 41a is sent to the heat absorbing head 54a through the blower 41d. The air sent to the heat absorbing head 54a is cooled and dehumidified by the heat absorbing head 54a, and then sent to the heat generating head 54b. The air sent to the heat generating head 54b is heated by the heat generating head 54b and blown into the water tank 3 through the air supply port described above to evaporate the moisture of the laundry in the rotating tank and proceed with drying. Let Thereafter, the end of drying is detected by detection of a humidity sensor or a temperature sensor (not shown), and the operation is terminated. A drainage hole (not shown) is provided at the bottom of the water tank back path 41c below the endothermic head 54a. When water (drain water) is condensed on the endothermic head 54a, the water tank back path 41c and the drainage are drained from this drain hole. Drained by a drain hose connecting hose 17.

[0162] As described above, according to the embodiment 2-2 of the present invention, in addition to the operation effect of the embodiment 2-2 described above, the direct drive type drive unit 40 provided on the back surface of the water tank 3 is provided. The heat exchange section 48 can be arranged in the lower empty space via the clutch mechanism so that the reverse Stirling cycle is substantially reversed V-shaped or eight-shaped, so that it is possible to provide a space-saving washing machine Touch with S.

[0163] In addition, in order to facilitate the removal of the laundry, when applied to the configuration of a drum-type washing machine in which the openings of the water tub 3 and the rotating tub 5 are disposed obliquely upward, The lower space of the main body 1 can be used effectively, and the center of gravity is lowered because the heat exchanging section 48 is disposed below the driving section 40. In addition, the heat absorption head 54a side and the heat generation head 54b side of the heat exchanging part 48 are arranged in a substantially reverse V order across the vertical center line passing through the motor shaft 58b of the heavy drive part 40. Therefore, it can also act as a vibration-proof weight, improving silence The power S

[0164] (Embodiment 2-3)

Hereinafter, Embodiment 2-3 of the present invention will be described with reference to FIGS. FIG. 27 is a cross-sectional view of the drum-type washer / dryer according to Embodiment 2-3 of the present invention, FIG. 28 is an enlarged view of the main part of FIG. 27, FIG. 29 is a cross-sectional view of FIG. FIG. 5 is an exploded perspective view of a configuration around a motor shaft 58b. In Embodiment 2-3, the same components as those in Embodiment 2-2 are given the same reference numerals and description thereof is omitted.

[0165] In Embodiments 2-3, a drive unit 58, which is an example of a motor, is provided on the back surface of the water tank 3. As shown in FIG. 28, the drive unit 58 is covered with a motor cover 58a, and a motor shaft 58b, one end of which is connected to the center of the back surface of the rotary tank 5, is rotated by the bearing 58c. It is supported freely. A motor 58e is attached to the other end of the motor shaft 58b, and has an outer rotor type direct drive system configuration in which a rotational driving force is applied by a stator 58d provided on the outer peripheral side thereof. Further, the motor shaft 58b is provided with a connecting portion 58f in which a part of the motor shaft 58b has a large diameter. As shown in FIG. 30, the connecting portion 58f is formed in a cross-shaped cross section so that a part thereof protrudes in the radial direction every 90 °.

[0166] On the outer periphery of the motor shaft 58b, as shown in FIG. 28, an interlocking shaft 59 is rotatably disposed adjacent to the connecting portion 58f. The interlocking shaft 59 is configured such that a portion adjacent to the connecting portion 58f has a small diameter and a portion away from the connecting portion 58f has a large diameter. The small-diameter portion 59a, which is the small-diameter portion of the interlocking shaft 59, is formed in a cross-shaped cross section so that a portion protrudes in the radial direction every 90 ° as shown in FIG. 30, and is formed in the same shape as the connecting portion 58f. Has been. On the other hand, the large-diameter portion 59b, which is the large-diameter portion of the interlocking shaft 59, is formed in a gear shape, and this gear is connected to a connecting gear 63 described later to transmit the rotational driving force. Yes.

[0167] As shown in FIG. 28, a clutch piece 60 is provided on the outer periphery of the connecting portion 58f. The clutch piece 60 is made of a magnetic material, and as shown in FIG. 30, the outer peripheral side is formed in a circular shape, and the inner peripheral side is partially recessed in the radial direction every 90 °. The outer periphery of the small-diameter portion 59a of the interlocking shaft 59 and the connecting portion 58f is configured to be formed on this inner peripheral side. A coil spring 61 is compressed between the large diameter portion 59b of the interlocking shaft 59 and the clutch piece 60. The clutch piece 60 is urged so as to be engaged with only the connecting portion 58f. On the outer peripheral side of the clutch piece 60, as shown in FIG. 28, a solenoid 62 for generating a magnetic force and generating a repulsive force on the clutch piece 60 is disposed. The solenoid 62 moves the clutch piece 60 against the urging force of the coil spring 61 by the drive, and engages the clutch piece 60 with both the connecting portion 58f and the interlocking shaft 59, thereby rotating the driving force of the motor shaft 58b. Is transmitted to a connecting gear 63 described later.

[0168] A connecting gear 63 is arranged below the large-diameter portion 59b of the interlocking shaft 59, as shown in FIG. The connecting gear 63 is connected to the gear of the large-diameter portion 59b of the interlocking shaft 59 above the connecting gear 63, and is also connected to the slide gear 64 arranged in the gear shaft direction. The slide gear 64 is coupled to the first small transmission gear 65 or the transmission gear 67 below the slide gear 64, and the first small transmission gear 65 is coupled to the second small transmission gear 66 below the slide gear 64. Further, the second small transmission gear 66 and the transmission gear 67 are connected to the crank gear 68 below the second transmission gear 66 and the transmission gear 67. The crank gear 68 is perpendicular to the surface opposite to the surface on which the small-diameter gear portion 68a (the broken line portion in FIG. 30), the disk-shaped large-diameter portion 68b, and the large-diameter gear portion are provided. It is composed of a cylindrical crankpin 68c that protrudes into the center. A heat exchanging section 48 is provided below the crank gear 68 as shown in FIG. In the present embodiment, the heat exchanging section 48 uses a V-type 2-biston Stirling refrigerator as in the embodiment 2-2. The interlocking shaft 59, clutch piece 60, coil spring 61, solenoid 62, coupling gear 63, slide gear 64, first small transmission gear 65, second small transmission gear 66, transmission gear 67, and crank gear 68 are described above. It is an example of a transmission part.

Here, the connection gear 63 and the slide gear 64 will be described with reference to FIG. 31 (a) is a top view of the slide gear 64, (b) is a view from the arrow F in (a), (c) is a view from the arrow G in (a), and (d) is a top view of the connecting gear 63. , (E) is a view taken along the arrow H in (d), (f) is a sectional view taken along the line I-I in (e), (g) is a sectional view taken along the line JJ in (e), and (h) is a sectional view taken along the KK in (e). Fig. (I) is an LL cross-sectional view of (e).

[0170] As shown in FIGS. 31 (a) to (c), the slide gear 64 includes a gear portion 64b, a cylindrical portion 64a extending in the gear axis direction from one side surface of the gear portion 64b, and a cylindrical portion 64a. It consists of a cylindrical pin part 64c extending from the tip in a direction perpendicular to the cylindrical axis, and a cylindrical pin part 64d extending in the opposite direction to the pin part 64c. As shown in FIGS. 31 (c!) To (i), the connecting gear 63 includes a gear portion 63b, a cylindrical portion 63a extending in the gear axis direction from one side surface of the gear portion 63b, and a cylindrical portion of the cylindrical portion 63a. The cylindrical part 64a is provided in the axial direction A hole 63c to be inserted, and a pin portion 64d of the slide gear 64 which is formed in a spiral shape perpendicularly to the peripheral surface of the hole 63c, is inserted, and the pin portion 64d is substantially around the cylinder axis of the cylinder portion 64a. A slide hole 63d formed so as to be slidable by 180 degrees, and a pin portion 64c of the slide gear 64 is inserted into a spiral shape perpendicularly to the peripheral surface of the hole portion 63c and the pin portion 64c is inserted into the cylindrical portion 64a. Consists of a slide hole 63e formed so that it can slide about 180 degrees around the cylinder axis

Next, the operation when the connecting gear 63 is given a rotational driving force from the interlocking shaft 59 will be described. First, when the connecting gear 63 is connected to the first small transmission gear 65, the connecting gear 63 receives a rotational driving force from the interlocking shaft 59, and rotates clockwise (clockwise) in FIG. 31 (e). When rotating in the direction, the pin part 64c slides the slide hole 63e, the pin part 64d slides the slide hole 63d about 180 degrees around the cylinder axis of the cylinder part 64a, and the cylinder part 64a slides in the direction that comes out of the hole part 63c. Moving. That is, the gear portion 64b slides toward the front side in FIG. 30 so that the connection with the first small transmission gear 65 is released and the transmission gear 67 is connected. Conversely, when the connecting gear 63 is connected to the transmission gear 67, the connecting gear 63 receives a rotational driving force from the interlocking shaft 59, and the counterclockwise direction in FIG. 31 (e) is counterclockwise. , The pin 64c slides the slide hole 63e, the pin 64d slides the slide hole 63d approximately 180 degrees around the cylinder axis of the cylinder 64a, and the cylinder 64a slides in the direction to enter the hole 63c. To do. That is, the gear portion 64b slides to the back side in FIG. 30 to release the connection with the transmission gear 67 and to connect with the first small transmission gear 65. In this way, regardless of whether the drive unit 58 rotates in the forward or reverse direction, the connection with the slide gear 64 is switched to the first small transmission gear 65 or the transmission gear 67 to thereby change the crank gear 68. The rotation direction can be a constant direction.

Next, the operation of the main part of the drying process of Embodiment 2-3 of the present invention will be described with reference to FIGS. 32 to 35. FIG. Fig. 32 is a cross-sectional view taken along the line E-E in Fig. 28, Fig. 33 is an enlarged view of the main part when the crank gear 68 is rotated 90 ° from the state of Fig. 32, and Fig. 34 is a crank gear from the state of Fig. 32. FIG. 35 is an enlarged view of the main part when the crank gear 68 is rotated by 270 ° from the state shown in FIG. 32. FIG.

[0173] When the drying process is started, the blower 41d is driven to blow air in the ventilation path 41. At the same time, the solenoid 62 is driven and the clutch piece 60 is engaged with the connecting portion 58f and the interlocking shaft 59, so that the rotational driving force of the driving portion 58 can be transmitted to the interlocking shaft 59. In this state, the rotational drive force of the drive unit 58 is changed from the interlocking shaft 59 → the connecting gear 63 → the slide gear 64 → the transmission gear 67 (or the first small transmission gear 65 → the second small transmission gear 66) → the crank gear 68. Is communicated to. As a result, the crank gear 68 rotates in the counterclockwise (counterclockwise) direction in FIG. 32 and the heat exchanging unit 48 is driven.

In the state of FIG. 32, while the crank gear 68 is driven counterclockwise (counterclockwise) and enters the state of FIG. 33, the endothermic crank 49a lifts the endothermic crosshead 50a upward. The heat generation side crank 49b is driven in a direction to push the heat generation side crosshead 50b downward, the heat absorption side piston 52a expands the gas in the low temperature chamber 53a, and the heat generation side piston 52b expands the gas in the high temperature chamber 53b. In order to compress the gas, the gas in the high temperature chamber 53b moves rapidly through the regenerator 57 to the low temperature chamber 53a. At this time, the amount of heat of the gas moving to the low temperature chamber 53a is stored in the regenerator 57, and the gas whose temperature has decreased is blown into the low temperature chamber 53a.

[0175] While the rotation of the crank gear 68 advances and the state of FIG. 33 shifts to the state of FIG. 34, the heat absorption side crank 49a and the heat generation side crank 49b are connected to the heat absorption side cross head 50a and the heat generation side cross. The head 50b is driven upward and the gas in the low temperature chamber 53a and the high temperature chamber 53b is expanded by the heat absorption side piston 52a and the heat generation side piston 52b. At this time, the expansion rate of the gas in the low temperature chamber 53a is much larger than that in the high temperature chamber 53b, and the pressure and temperature of the gas in the low temperature chamber 53a decrease, so the temperature of the endothermic head 54a decreases.

[0176] While the rotation of the crank gear 68 advances and the state of FIG. 34 shifts to the state of FIG. 35, the heat absorption side crank 49a pushes the heat absorption side crosshead 50a downward, and the heat generation side crank 49b drives the heat generating side cross head 50b to lift upward, compresses the gas in the low temperature chamber 53a by the heat absorption side piston 52a, and expands the gas in the high temperature chamber 53b by the heat generation side piston 52b. The gas rapidly moves through the regenerator 57 to the high temperature chamber 53b. At this time, the gas moving to the high temperature chamber 53b is heated by the amount of heat stored in the regenerator 57, the temperature rises, and the temperature in the high temperature chamber 53b rises.

[0177] While the rotation of the crank gear 68 proceeds, the state shown in FIG. 35 changes to the state shown in FIG. The endothermic side crank 49a and the exothermic side crank 49b drive the endothermic side crosshead 50a and the exothermic side crosshead 50b in a downward direction so that the endothermic side piston 52a and the exothermic side piston 52b drive the inside of the low temperature chamber 53a and the high temperature. Compress the gas in chamber 53b. At this time, the compressibility of the gas in the high temperature chamber 53b is much larger than that in the low temperature chamber 53a, and the pressure and temperature of the gas in the high temperature chamber 53b rise, so the temperature of the heating head 54b rises and the high pressure in the high temperature chamber 53b increases. Then, the gas whose temperature has increased is blown into the low temperature chamber 53a through the regenerator 57. When the gas whose temperature has been increased due to the high pressure in the high temperature chamber 53b passes through the regenerator 57, the heat quantity of this gas is stored in the regenerator 57, and the cooled gas is blown into the low temperature chamber 53a. To lower the temperature of the cold chamber 53a. As the crank gear 68 rotates in this manner, the heat absorbing head 54a cools and the heat generating head 54b generates heat, and the temperature decreases and rises according to the rotational speed of the crank gear 68, respectively.

[0178] In the drying process, the air discharged from the water tank 3 into the ventilation path 41 through the exhaust port 41a is sent to the heat absorbing head 54a through the blower 41d. The air sent to the heat absorbing head 54a is cooled and dehumidified by the heat absorbing head 54a, and then sent to the heat generating head 54b. The air sent to the heat generating head 54b is heated by the heat generating head 54b and blown into the water tub 3 to evaporate the moisture in the laundry in the rotating tub and to proceed with drying. Thereafter, the end of drying is detected by detection of a humidity sensor or a temperature sensor (not shown) and the operation is terminated. A drain hole (not shown) is provided at the bottom of the water tank back path 41c below the heat absorbing head 54a. When water (drain water) condensed on the heat absorbing head 54a drops, the water tank back path 41c and the drain hose are drained from this drain hole. Drained by a drain hose connecting 17.

As described above, according to Embodiment 2-3 of the present invention, in addition to the operational effects of Embodiments 2-1 and 2-2 described above, even if the drive unit 58 is rotated forward and backward, The direction of rotation of the crank gear 68 that drives the exchanging section 48 can be made constant. Thus, for example, in the drying process, even if the rotating tub 5 is rotated forward and backward in order to release the entanglement of clothing etc., the heat exchanging part 48 can continue the reverse Stirling cycle. Drying time can be shortened.

[0180] Further, according to Embodiments 2— ;! to 2-3 of the present invention, for example, an electric heater is used for heating the circulating air to dry the laundry, and tap water is used for cooling and dehumidifying the circulating air. Conventional technique used Compared with the technology, the power used is only the driving power of the motor, and the power consumption can be further reduced. In addition, the amount of tap water used can be reduced.

[0181] In addition, according to Embodiments 2—;! To 2-3 of the present invention, for example, compared to the conventional technology using a heat pump for heating the circulating air for drying laundry and cooling and dehumidifying the circulating air Thus, the power used is only the driving power of the motor, and power S can be used to achieve a further reduction in power consumption.

[0182] According to Embodiments 2—;! To 2-3 of the present invention, the laundry can be dried or the laundry can be 'dehydrated' and dried with the driving power of the motor that rotates the rotating tub. Compared to other dryers or laundry dryers, it is possible to achieve further reductions in water consumption and power consumption.

[0183] In particular, when a Stirling refrigerator is used as the heat exchange unit, a reverse Stirling cycle is performed by an interlocking means that transmits the rotational power of the motor to the Stirling refrigerator, and the low temperature chamber of the Stirling refrigerator is connected. Using a high greenhouse, drying of the laundry can be realized by heating the circulating air to dry the laundry and cooling and dehumidifying the hot and humid circulating air containing moisture evaporated from the laundry.

[0184] Therefore, it is possible to provide a dryer or a washing dryer that can further reduce power consumption without using water.

[0185] The above-described configuration and control are not limited to the washing and drying machine, and the rotation tank that can be applied to the drying machine is not limited to the horizontal type, and may be a vertical type. Not limited to formulas.

[0186] The technical idea of the dryer based on Embodiment 2— ;! to 2-3 of the present invention is summarized as follows.

[0187] (1) A dryer according to the present invention includes a water tank, and a rotary tank rotatably provided in the water tank.

A motor that rotates the rotating tank, a circulation duct that communicates with the inside of the water tank, a fan that circulates the gas in the water tank through the circulation duct, and the air in the circulation duct is cooled by an endothermic head. A heat exchanging unit that exchanges heat so as to heat; and a transmission unit that transmits the rotational force of the motor as power for operating the heat exchanging unit.

[0188] (2) The dryer according to the present invention is characterized in that the heat exchange section is provided in a water tank.

[0189] (3) In the dryer according to the present invention, the heat exchange section is provided below the water tank. It is characterized by being.

(4) The dryer according to the present invention is characterized in that the heat exchange section is provided on the back surface of the water tank.

[0191] (5) In the dryer according to the present invention, the heat exchanging section is provided below the motor.

[0192] (6) The dryer according to the present invention is characterized in that at least a part of the circulation duct is disposed below the water tank.

[0193] (7) In the dryer according to the present invention, at least a part of the circulation duct is disposed on the back surface of the water tank.

(8) In the dryer according to the present invention, at least a part of the circulation duct is arranged along the peripheral edge of the back surface of the water tank.

(9) The dryer according to the present invention is characterized in that a part of the circulation duct is arranged between the heat exchange part and a part of the drainage path for draining the liquid in the water tank.

(10) The dryer according to the present invention is characterized in that the heat absorbing head and the heat generating head protrude into the circulation duct.

(11) In the dryer according to the present invention, the heat exchange section is a Stirling refrigerator.

[0198] (12) In the dryer according to the present invention, the Stirling refrigerator includes a semi-hermetic housing, a crankshaft disposed in the housing, and a heat absorption side crank connected to the crankshaft. A heat generating side crank, a heat absorbing side piston connected to each crank, a heat generating side piston, a working gas is sealed inside, and a low temperature chamber and a high temperature chamber in which each piston reciprocates in conjunction with rotation of the crankshaft, The crankshaft is rotated by the transmission unit.

[0199] (13) In the dryer according to the present invention, the heat absorbing head and the heat generating head are a low temperature chamber and a part of the high temperature chamber which appear and disappear in the circulation dirt.

(14) In the dryer according to the present invention, the transmission unit includes an interlocking shaft that engages with the rotation shaft of the motor via a clutch, and a gear that is connected to the interlocking shaft and rotates the crankshaft. It is characterized by having.

[0201] (15) In the dryer according to the present invention, the transmission section is configured so that the rotation of the motor is normal or Is characterized by rotating the crankshaft in one direction even if it rotates in the reverse direction.

[0202] (16) In the dryer according to the present invention, the transmission unit transmits the rotational force of the motor to the crankshaft, and operates the Stirling refrigerator in a reverse Stirling cycle.

[0203] (17) The dryer according to the present invention is characterized in that each piston reciprocates with a phase difference of 90 degrees.

[0204] (18) In the dryer according to the present invention, the clutch is arranged between the first fitting portion provided on the rotating shaft of the motor and the second fitting portion provided on the interlocking shaft. The urging means for urging the clutch toward the first fitting portion side is arranged between the clutch and the interlocking shaft.

(19) The dryer according to the present invention is provided with an electromagnetic coil that generates a magnetic field around the clutch, and energizes the electromagnetic coil so that the clutch is engaged with the first fitting portion and the second fitting portion. It is characterized in that it is moved to a position that fits both parts.

(20) In the dryer according to the present invention, the gear meshes with the first transmission gear meshed with the interlocking shaft, the first transmission gear and the crank gear provided on the crankshaft, and the motor It is characterized by comprising a second transmission gear that rotates in the direction opposite to the rotation axis.

[0207] (21) In the dryer according to the present invention, the crankshaft is provided on one of the crankshaft and the crankshaft in which the connecting portions to which the respective cranks are connected are provided with a phase difference of 90 degrees. The second transmission gear is composed of a small-diameter gear and a large-diameter gear, the first transmission gear and the small-diameter gear are combined, and the crank gear and the large-diameter gear are combined. It is characterized by being arranged!

[0208] (22) In the dryer according to the present invention, the crankshaft is provided with a pin connected to each crank on one side and a crank gear meshed with the gear on the other! /.

[0209] (23) In the dryer according to the present invention, the first transmission gear includes an interlocking gear that is always connected to the interlocking shaft, and a slide gear that is provided with the rotation center and position of the interlocking gear overlapped with each other. The slide gear is configured to be variable in distance to the interlocking gear according to the rotation direction of the interlocking gear, and the second transmission gear is always meshed with the crank gear, and the rotational position is When the interlocking gear rotates in one direction, the slide gear is connected to the transmission gear and the interlocking gear rotates in the other direction. In some cases, the slide gear is connected to the small transmission gear.

[0210] (24) In the dryer according to the present invention, the low-temperature chamber and the high-temperature chamber are arranged in an eight-letter shape or an inverted V-shape when viewed from the center of the rotation shaft of the motor. Features.

[0211] (25) A laundry dryer according to the present invention is any one of the above-described dryers, wherein the object to be cleaned is accommodated in a rotating tub, and any one of washing, dehydration, and drying is performed. It is characterized by.

[0212] (26) In the washing and drying machine according to the present invention, the rotation axis of the rotating tub is substantially perpendicular to the installation surface.

[0213] (27) In the washing and drying machine according to the present invention, the rotation axis of the rotating tub is substantially horizontal or oblique to the installation surface.

Example

[0214] The high controllability obtained by using an example of the Stirling engine used in the dryer according to one embodiment of the present invention will be described.

[0215] The characteristics of the Stirling engine and the heat pump were checked by driving the Stirling engine and the heat pump under atmospheric pressure and opening the high temperature side and the low temperature side to the atmosphere. The temperature on the high temperature side of the Stirling engine was measured with a heating head and the temperature on the low temperature side was measured with a heat absorption head. The temperature on the high temperature side of the heat pump was measured using a condenser, and the temperature on the low temperature side was measured using an evaporator. The measured temperature was recorded every 10 seconds. The room temperature was about 27 ° C. The Stirling engine used as an example has an output of about 250 W and the refrigerant is helium. The specification of the heat pump used as an example is an output of about 370 W, and the refrigerant is HCF'R134a.

[0216] FIG. 36 is a diagram showing a temporal change in temperature on the high temperature side measured immediately after the start of driving of the Stirling engine and the heat pump.

[0217] As shown in Fig. 36, in the high temperature part of the Stirling engine, the temperature has risen immediately after the start of the Stirling engine drive. On the other hand, the temperature of the high-temperature part of the heat pump hardly changes immediately after the start of driving the heat pump and starts to rise slowly after about 10 seconds. [0218] FIG. 37 is a diagram showing a temporal change in temperature on the high temperature side from the start of driving of the Stirling engine and the heat pump until reaching a predetermined temperature. The prescribed temperature was 60 ° C.

[0219] As shown in Fig. 37, the high temperature side of the Stirling engine reached 60 ° C in 50 seconds from the start of driving. On the other hand, the high temperature side of the heat pump reached 60 ° C in 230 seconds from the start of driving. In this way, the high temperature side of the Stirling engine reaches a predetermined temperature faster than the high temperature side of the heat pump, so by using the Stirling engine in the dryer, the high temperature gas is washed in the initial stage of the drying process. The force S can be used to reduce the drying time.

[0220] Fig. 38 is a diagram showing a temporal change in temperature that changes in 10 seconds with respect to the temperature on the high temperature side measured immediately after the start of driving of the Stirling engine and the heat pump.

[0221] As shown in FIG. 38, it was found that the Stirling engine has a large responsiveness with a large temperature change immediately after the start of driving. On the other hand, the temperature change of the heat pump was hardly measured immediately after the start of driving. This is because a certain amount of time is required for the heat pump refrigerant to change state between the gas and liquid phases, while the Stirling engine does not require the operating gas to change state. It is thought that sex was obtained.

[0222] Figure 39 shows the temperature of the high and low temperature sides of the Stirling engine and the high and low temperature sides of the heat pump measured at 10-second intervals immediately after the start of driving the Stirling engine and heat pump. It is a figure which shows a change.

[0223] As shown in Fig. 39, immediately after the start of the Stirling engine drive, the temperature on the high temperature side of the Stirling engine rises quickly, and the temperature on the low temperature side of the Stirling engine falls quickly, and the drive starts. 50 seconds later, the high temperature reached 60 ° C and the low temperature reached 20 ° C. After that, 2 minutes after the start of driving, the speed of temperature change hardly decreased, and the high temperature side reached 80 ° C and the low temperature side reached 60 ° C. On the other hand, the heat pump is about 35 ° C on the high temperature side and about 10 ° C on the low temperature side from about 10 seconds to 30 seconds after the start of driving, where there is almost no temperature change on the high temperature side and low temperature side immediately after the start of driving. After that, the temperature change decreased and showed a gradual temperature change. The temperature on the high temperature side gradually increased and reached about 48 ° C from the start of driving for 2 minutes, and the temperature on the low temperature side hardly decreased from about 8 ° C. [0224] Thus, the responsiveness of the Stirling engine is higher than that of the heat pump. A Stirling engine has a wider controllable temperature range than a heat pump. For example, the time required for the high temperature side to reach 60 ° C after starting the steering engine is four times the time required for the high temperature side to reach 60 ° C after starting the heat pump. It was less than a fraction. Therefore, by using a Stirling engine, a dryer having higher controllability than a heat pump can be obtained. In this way, a dryer equipped with a Stirling engine can shorten the time required to start up the dryer, and the time required to start up again after interrupting the operation once during the operation of the dryer is also reduced. can do

Yes

[0225] The embodiments and examples disclosed above are to be considered in all respects as illustrative and not restrictive. The scope of the present invention is shown by the claims which are not described in the above embodiments and examples, and includes all modifications and variations within the meaning and scope equivalent to the claims.

Industrial applicability

[0226] By applying the dryer of the present invention to a washing dryer for drying clothes and the like, it is possible to dry an object to be dried such as clothes while suppressing noise.

Claims

The scope of the claims

A container (230) for containing an object to be dried;

A circulation path (241, 242, 243) for allowing the gas flowing out from the inside of the container (230) to flow into the container (230);

A first heat exchange section (420) for heating the gas flowing through the circulation path (241, 242, 243);

A second heat exchange section (243) for cooling the gas flowing through the circulation path (241, 242, 243);

A Stirling engine (410) including a heat generating head (411) and a heat absorbing head (412) is provided. The first heat exchanging part (420) includes a heat generating head (41) of the Stirling engine (410).

Perform heat exchange to heat the gas in 1),

The second heat exchanging unit (430) includes a heat absorbing head (41) of the Stirling engine (410).

A dryer (200) that exchanges heat to cool the gas in 2).

The container (230) is disposed so as to cover the water tank (220) for containing water, and the container (230) is rotatably supported in the water tank (220). The dryer according to claim 1, wherein the object to be dried contained in the container (230) is configured to be washable in the container (230). 200)

Yes

The dryer (200) according to claim 1, wherein the heat generating head (411) is disposed in the circulation path (241, 242, 243) and constitutes the first heat exchange section (420).

The dryer (200) according to claim 1, wherein the endothermic head (412) is disposed in the circulation path (241, 242, 243) and constitutes the second heat exchange section (430).

The heat generating head (411) is disposed in the circulation path (241, 242, 243) to constitute the first heat exchanging part (420),

A connecting pipe (148) disposed between the heat generating head (411) and the heat absorbing head (412) is provided. Prepared,

The connecting pipe (148) is disposed coaxially with the heat generating head (411) and the heat absorbing head (412),

The dryer (200) according to claim 5, wherein the heat generating head (411), the heat absorbing head (412), and the connecting pipe (148) are disposed in the circulation path (241, 242, 243). .