WO2012144122A1 - 衛生洗浄装置 - Google Patents

衛生洗浄装置 Download PDF

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Publication number
WO2012144122A1
WO2012144122A1 PCT/JP2012/001522 JP2012001522W WO2012144122A1 WO 2012144122 A1 WO2012144122 A1 WO 2012144122A1 JP 2012001522 W JP2012001522 W JP 2012001522W WO 2012144122 A1 WO2012144122 A1 WO 2012144122A1
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WO
WIPO (PCT)
Prior art keywords
flow path
heat transfer
heater
inflow portion
water
Prior art date
Application number
PCT/JP2012/001522
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
良一 古閑
Original Assignee
パナソニック株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2011095749A external-priority patent/JP5786129B2/ja
Application filed by パナソニック株式会社 filed Critical パナソニック株式会社
Priority to CN201280000811.0A priority Critical patent/CN102859086B/zh
Priority to KR1020127022666A priority patent/KR101399717B1/ko
Publication of WO2012144122A1 publication Critical patent/WO2012144122A1/ja

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/10—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/10—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium
    • F24H1/101—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium using electric energy supply
    • F24H1/102—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium using electric energy supply with resistance
    • F24H1/103—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium using electric energy supply with resistance with bare resistances in direct contact with the fluid
    • E—FIXED CONSTRUCTIONS
    • E03—WATER SUPPLY; SEWERAGE
    • E03D—WATER-CLOSETS OR URINALS WITH FLUSHING DEVICES; FLUSHING VALVES THEREFOR
    • E03D9/00—Sanitary or other accessories for lavatories ; Devices for cleaning or disinfecting the toilet room or the toilet bowl; Devices for eliminating smells
    • E03D9/08—Devices in the bowl producing upwardly-directed sprays; Modifications of the bowl for use with such devices ; Bidets; Combinations of bowls with urinals or bidets; Hot-air or other devices mounted in or on the bowl, urinal or bidet for cleaning or disinfecting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/0092—Devices for preventing or removing corrosion, slime or scale
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/14—Arrangements for connecting different sections, e.g. in water heaters 
    • F24H9/146—Connecting elements of a heat exchanger

Definitions

  • the present invention relates to a sanitary washing apparatus, and more particularly, to a sanitary washing apparatus having a nozzle that ejects hot water.
  • a flat heater is accommodated vertically in a rectangular parallelepiped casing having a small thickness.
  • Two flow paths are formed along each of the heat transfer surfaces of the flat heater so as to meander upward in the horizontal direction. While the flat heater is driven, the washing water flows along each flow path, and the temperature is raised to an appropriate temperature (see, for example, Patent Document 1).
  • the flat heater becomes locally hot due to the scale, a temperature difference occurs in the flat heater. Due to the thermal stress due to this temperature difference, in a flat plate heater using ceramics as a heating element, the flat plate heater is cracked or broken, and the flat plate heater fails.
  • the present invention has been made to solve such a problem, and an object of the present invention is to provide a sanitary washing apparatus capable of ensuring a necessary flow rate of washing water and preventing failure.
  • a sanitary washing device has a nozzle, an upstream end to be connected to a water supply source, and a water supply path whose downstream end is connected to the nozzle, and heat exchange provided in the water supply path
  • the heat exchanger includes an inflow portion, an outflow portion located above the inflow portion, a lower end portion communicated with the inflow portion, an upper end portion communicated with the outflow portion, and a vertical direction.
  • a plate-like heater housing space formed to extend to the heater, and heat transfer that is accommodated in the heater housing space of the casing so as to extend in the vertical direction and faces the main surface of the heater housing space
  • a flat plate-like heater including a surface, and a flow path space formed in a gap between the heat transfer surface and the main surface of the heater housing space, and the flow path space is formed on the inflow portion side.
  • the width of the gap is smaller than the width of the gap on the outflow portion side. It is formed in so that.
  • the present invention has the above-described configuration, and has an effect that it is possible to provide a sanitary washing device that can secure a necessary flow rate of washing water and prevent failure.
  • FIG. 3 is a cross-sectional view showing the heat exchanger cut along line AA in FIG. 2.
  • FIG. 4 is a longitudinal sectional view showing a heat exchanger cut along a line BB in FIG. 3. It is an enlarged view of the area
  • the present inventors examined a heat exchanger in which a flow path was formed along both heat transfer surfaces of a flat heater.
  • heat exchangers are designed on the assumption that the heat transfer amounts on both heat transfer surfaces to the wash water are approximately the same. If there is a large difference in the amount of heat transfer on both sides, a local boiling phenomenon may occur in the flow path on one side, and bubbles may be generated. Such bubbles increase the flow resistance of the washing water in the flow path, the flow rate balance in both flow paths is lost, and the difference in the amount of heat transfer becomes larger.
  • a temperature sensor such as a thermistor may be provided near the water outlet of the heat exchanger. In this case, if bubbles grow large and adhere to the temperature sensor, the temperature sensor cannot contact the cleaning water. For this reason, a temperature sensor cannot detect appropriately.
  • the bubbles adhere to the heat transfer surface and grow large, the bubbles are interposed between the heat transfer surface and the washing water, and both are dissociated. In this case, it becomes difficult to transfer heat from the heat transfer surface to the washing water, and the temperature of the heat transfer surface increases greatly. The temperature difference between the heat transfer surface to which bubbles are attached and the opposite heat transfer surface is increased. Due to the thermal stress, the flat heater is deformed and the life of the heat exchanger is shortened.
  • the most dominant factor that the scale adheres to the heat transfer surface is the temperature of the heat transfer surface.
  • the set temperature of the heat transfer surface is determined to be 100 ° C. or lower, preferably 80 ° C. or lower, at which boiling occurs.
  • the set temperature of the heat transfer surface is appropriately determined by the scale concentration of tap water, the required durability time of the heater, and the like. If a part of the heat transfer surface exceeds the set temperature, the scale adheres to that part and the scale becomes an obstacle to heat transfer. In order to avoid this, the area of the heat transfer surface may be increased. However, this is not preferable because it increases the cost of the heat exchanger.
  • the watt density or heat transfer coefficient distribution of the flat heater so that the temperature of the heat transfer surface is substantially uniform as a whole.
  • the size of the heat transfer surface is minimum, and the temperature of the heat transfer surface can be set to a set temperature or less, but the cost of the flat heater is increased.
  • the flow path thickness is very thin, local non-uniformity in the flow velocity tends to occur. Since the thickness of the flow path: 0.5 mm is smaller than the order of the thickness of the speed boundary layer: several mm, the speed boundary layer covers the entire flow path. Therefore, the velocity gradient changes depending on the channel thickness, and the non-uniform flow velocity is likely to occur due to the non-uniform channel thickness.
  • the velocity boundary layer is a fluid layer where the velocity is zero on the heat transfer surface and the velocity changes rapidly. For this reason, the force which discharges the bubble on a heat-transfer surface from on a heat-transfer surface is weak. Further, when the channel thickness is small, the size of bubbles generated in the channel tends to be larger than the channel thickness. In this case, the foam is deformed corresponding to the thickness of the flow path, and a push-up force is generated by the surface tension of the foam, so that the foam is difficult to move. Therefore, bubbles stay in the flow path, and unevenness of the flow rate tends to be locally generated by the bubbles.
  • the heat transfer surface temperature rises significantly locally in a flat watt heater with a high watt density such that the watt density is 30 W / cm 2 or more. Boiling occurs at this point, and bubbles are further generated. For this reason, the non-uniformity of the flow is promoted, and the heat transfer surface is burned out.
  • the heat exchanger becomes compact and the heat transfer area can be easily increased.
  • the flow tends to be non-uniform. For this reason, when a superheated part is produced partially, heat concentrates on this superheated part, the washing water of this part evaporates, and a bubble is produced. If the bubbles do not flow out, this part is further heated. As a result, when the bubbles become large and the heat transfer surface becomes extremely hot, the heater is destroyed.
  • the present invention has been made based on the above findings.
  • a sanitary washing device has a nozzle, an upstream end to be connected to a water supply source, and a water supply path whose downstream end is connected to the nozzle, and heat exchange provided in the water supply path
  • the heat exchanger includes an inflow portion, an outflow portion located above the inflow portion, a lower end portion communicated with the inflow portion, an upper end portion communicated with the outflow portion, and a vertical direction.
  • a plate-like heater housing space formed to extend to the heater, and heat transfer that is accommodated in the heater housing space of the casing so as to extend in the vertical direction and faces the main surface of the heater housing space
  • a flat plate-like heater including a surface, and a flow path space formed in a gap between the heat transfer surface and the main surface of the heater housing space, and the flow path space is formed on the inflow portion side.
  • the width of the gap is smaller than the width of the gap on the outflow portion side. It is formed in so that.
  • the flat heater may be configured such that the heat generation density on the inflow portion side is larger than the heat generation density on the outflow portion side.
  • the flat heater includes a ceramic base and a heating wire formed by pattern printing on the ceramic base, and a cross-sectional area of the heating wire on the inflow portion side is the outflow It may be smaller than the cross-sectional area of the heating wire on the part side.
  • the flat heater includes a ceramic base and a heating wire formed by pattern printing on the ceramic base, and an interval between the heating wires adjacent to each other on the inflow portion side is as follows. It may be larger than the interval between the heating wires adjacent to each other on the outflow portion side.
  • the heat exchanger further includes a water inlet, and a header portion formed between the water inlet and the inflow portion.
  • a throttle channel that gradually narrows toward the inflow portion.
  • the Z direction shown in each drawing indicates the vertical direction.
  • the X direction indicates a direction orthogonal to the vertical direction and parallel to the heat transfer surfaces 20 a and 20 b of the flat heater 20.
  • the Y direction indicates a direction orthogonal to both the Z direction and the X direction.
  • the cross-sectional area indicates an area in a plane perpendicular to the flow of the cleaning water.
  • FIG. 9 is a schematic diagram illustrating a main configuration of the sanitary washing device 1 according to the first embodiment.
  • the sanitary washing device 1 includes a nozzle 7, a water supply path 9 having an upstream end to be connected to the water supply source 8, and a downstream end connected to the nozzle 7, and a heat exchanger 10 provided in the water supply path 9. Prepare.
  • FIG. 10 is a cross-sectional view showing the heat exchanger 10 mounted on the sanitary washing device 1 of FIG.
  • the heat exchanger 10 has an inflow portion 10a, an outflow portion 10b positioned above the inflow portion 10a, a lower end portion that communicates with the inflow portion 10a, an upper end portion that communicates with the outflow portion 10b, and extends vertically.
  • a casing 23 including a plate-shaped heater housing space 23c formed therein, and is accommodated in the heater housing space 23c of the casing 23 so as to extend in the vertical direction, and is opposed to the main surfaces 30a and 40a of the heater housing space 23c.
  • a flow path space 25 formed in a gap between the heat transfer surfaces 20a and 20b and the main surfaces 30a and 40a of the heater accommodating space 23c.
  • the flow path space 25 is formed such that the width of the gap on the inflow portion 10a side is smaller than the width of the gap on the outflow portion 10b side.
  • the “vertical direction” is a concept including both the vertical direction and the direction intersecting the vertical direction.
  • the “heater accommodating space” means a space including a region where the heater is present and a space in contact with the region, assuming that the heater is removed from the casing.
  • the “flow path space” is a flow path formed so as to guide a fluid (here, water) along the pair of heat transfer surfaces of the flat heater in the casing.
  • the washing water flows from the water supply source 8 through the water supply passage 9. Wash water flows into the heat exchanger 10 in the water supply channel 9 and is heated here. The wash water that has reached a high temperature flows out of the heat exchanger 10 and is supplied to the nozzle 7. Thereby, hot water is ejected from the nozzle 7.
  • the washing water flows into the heater accommodating space 23c of the casing 23 from the inflow portion 10a.
  • the washing water enters between the planar main surfaces 30 a and 40 a of the heater housing space 23 c and the heat transfer surfaces 20 a and 20 b of the flat heater 20 and passes through the flow path space 25. At this time, the washing water is heated by the heat transfer surfaces 20a and 20b, and the temperature rises.
  • the width of the gap on the inflow portion 10a side is smaller than the width of the gap on the outflow portion 10b side. For this reason, the cleaning water flowing through the flow path space 25 is accelerated in forced convection on the inflow portion 10a side.
  • the velocity gradient of the boundary layer between the heat transfer surfaces 20a and 20b and the washing water increases, and the heat transfer coefficient increases. Heat is applied to the washing water from the heat transfer surfaces 20a and 20b, the temperature of the heat transfer surfaces 20a and 20b is low, and scales are prevented from adhering to the heat transfer surfaces 20a and 20b.
  • Wash water flows from the inflow portion 10a side to the outflow portion 10b side by forced convection.
  • the washing water is further heated by the heat transfer surfaces 20a and 20b on the outflow portion 10b side.
  • the air mixed in the cleaning water expands and bubbles are generated. Since the width of the gap on the outflow portion 10b side is large, the bubbles exit to the outflow portion 10b without staying in the flow path space 25.
  • the temperature of the washing water rises and the density thereof decreases, so that an upward flow of natural convection occurs, and the washing water flows to the outflow portion 10b. Since the width of the gap on the outflow portion 10b side is large, bubbles are easily removed by the upward flow of natural convection, and the heat transfer rate from the heat transfer surfaces 20a, 20b to the washing water is improved.
  • the bubbles are smoothly discharged, so that heat exchange between the washing water and the heat transfer surfaces 20a and 20b is stably performed without being inhibited by the bubbles.
  • bubbles do not adhere to the heat transfer surfaces 20a and 20b, and this portion is heated to prevent a temperature difference between the heat transfer surfaces 20a and 20b. Thereby, it can prevent that the heat-transfer surfaces 20a and 20b are not deform
  • FIG. 1 shows a toilet in which a sanitary washing device 1 according to Embodiment 2 is attached to a toilet bowl 2.
  • the sanitary washing device 1 is disposed on the upper surface of the toilet bowl 2.
  • the sanitary washing device 1 includes a main body part 3, a toilet seat part 4, a toilet lid part 5, and an operation part 6.
  • the main body 3 is disposed on the rear side of the toilet seat 4, that is, on the rear side as viewed from the seated user.
  • the main body 3 is a horizontally long casing 3a and houses the water supply passage 9 and the heat exchanger 10 shown in FIG.
  • the main body unit 3 houses a cleaning unit, a drying unit, a control unit for controlling these operations, and the like (not shown).
  • the water supply channel 9 introduces tap water (fluid, liquid, washing water) into the nozzle 7 through the heat exchanger 10 from a water supply facility (water supply source 8) attached to the building where the toilet 2 is installed.
  • a water supply facility water supply source 8
  • the cleaning unit is driven. Washing water is warmed by the heat exchanger 10, and the hot water is discharged from the nozzle 7 in a shower shape toward the opening of the toilet 2.
  • FIG. 2 is a plan view showing the front of the heat exchanger 10.
  • FIG. 3 is a plan view showing the right main surface of the heat exchanger 10.
  • FIG. 4 is a cross-sectional view showing the heat exchanger 10 cut along the line AA in FIG.
  • FIG. 5 is a longitudinal sectional view showing the heat exchanger 10 cut along the line BB in FIG. 6 is an enlarged view of a region C in FIG.
  • the heat exchanger 10 has a small thickness in the Y direction and a rectangular shape in the XZ direction. As shown in FIG. 4, the heat exchanger 10 includes a flat heater 20, a first flow path forming member 21, and a second flow path forming member 22.
  • a casing 23 is formed by the first flow path forming member 21 and the second flow path forming member 22.
  • the first flow path forming member 21 and the second flow path forming member 22 are each formed of, for example, a reinforced ABS resin obtained by compounding a glass fiber with an ABS resin.
  • the first flow path forming member 21 is disposed on the first heat transfer surface 20a side of the flat heater 20.
  • the first flow path forming member 21 includes a base portion 30 and a shelf step portion 31.
  • the base portion 30 includes a base surface (main surface) 30a.
  • the base surface 30a has a planar shape and faces the first heat transfer surface 20a.
  • the thickness of the base portion 30 in the Y direction changes.
  • the thickness of the base 30 on the outflow part 10 b side from the shelf step part 31 is smaller than the inflow part 10 a side from the shelf step part 31.
  • the base surface 30a on the inflow portion 10a side from the shelf step portion 31 is closer to the first heat transfer surface 20a than the base surface 30a on the outflow portion 10b side.
  • the width between the base surface 30a on the inflow portion 10a side and the first heat transfer surface 20a is narrower than the width between the base surface 30a on the outflow portion 10b side and the first heat transfer surface 20a.
  • the first flow path forming member 21 is provided with a wall-like flange portion 32 around the entire periphery of the base portion 30.
  • An engagement groove 33 is formed at the distal end of the flange portion 32, and the engagement groove 33 is formed along the entire circumference of the flange portion 32.
  • the second flow path forming member 22 is disposed on the second heat transfer surface 20 b side of the flat heater 20.
  • the second flow path forming member 22 includes a base portion 40 and a shelf step portion 41.
  • the base portion 40 includes a base surface (main surface) 40a.
  • the base surface 40a has a planar shape and faces the second heat transfer surface 20b.
  • the thickness of the base portion 40 in the Y direction changes.
  • the thickness of the base portion 40 on the outflow portion 10b side from the shelf step portion 41 is smaller than the shelf step portion 41 on the inflow portion 10a side.
  • the base surface 40a on the inflow portion side from the shelf step portion 41 is closer to the second heat transfer surface 20b than the base surface 40a on the outflow portion 10b side.
  • the width between the base surface 40a on the inflow portion 10a side and the second heat transfer surface 20b is narrower than the width between the base surface 40a on the outflow portion 10b side and the second heat transfer surface 20b.
  • the second flow path forming member 22 is provided with a wall-like flange portion 42 around the entire periphery of the base portion 40.
  • the flange part 42 protrudes toward the opposite side of the base surface 40a.
  • tip part of the flange part 42 is return
  • An engagement protrusion 43 is provided at the tip of the tip, and the engagement protrusion 43 is formed over the entire circumference of the flange portion 42.
  • the flange portion 42 of the second flow path forming member 22 enters the flange portion 32 of the first flow path forming member 21, and the engaging protrusion of the second flow path forming member 22 enters the engaging groove 33 of the first flow path forming member 21. 43 fits.
  • the engagement protrusion 43 is fixed to the engagement groove 33 by ultrasonic welding. Thereby, the 1st flow path formation member 21 and the 2nd flow path formation member 22 are watertightly joined, and the casing 23 is formed.
  • the casing 23 has two side surfaces, two main surfaces, a top surface, and a bottom surface, and includes a substantially rectangular hollow portion surrounded by these. This substantially rectangular hollow portion constitutes a plate-shaped heater accommodating space 23c.
  • the heater housing space 23c extends in the vertical direction.
  • the lower end portion of the heater accommodating space 23c communicates with the inflow portion 10a, and the upper end portion communicates with the outflow portion 10b.
  • the water inlet 23a and the water outlet 23b open on one side.
  • the opening of the water outlet 23b becomes the outflow part 10b.
  • the water inlet 23a is provided at one end lower portion of the side surface, and is connected to the upstream end of the water supply channel 9 (FIG. 9).
  • the water outlet 23b is provided at the upper end of the side surface and is connected to the downstream end of the water supply channel 9 (FIG. 9).
  • Two main surfaces in the XZ direction are formed by base surfaces 30a and 40a, respectively.
  • the top surface faces the upper end of the flat heater 20.
  • the top surface is inclined so that the gap between the top surface and the upper end of the flat heater 20 becomes wider as it approaches the water outlet 23b.
  • the bottom surface faces the lower end of the flat heater 20.
  • the inflow portion 10a of the flow path space 25 opens on the top surface, and the inflow portion 10a extends in the X direction.
  • a flow path space 25 and a header portion 45 are formed inside the casing 23.
  • the flow path space 25 includes a flow path between the first heat transfer surface 20a and the base surface 30a and a flow path between the second heat transfer surface 20b and the base surface 40a. These two flow paths are formed symmetrically on both sides of the flat heater 20.
  • Each of the two channels has an inlet side channel 25a and an outlet side channel 25b.
  • the inlet-side flow path 25a is provided on the side closer to the water inlet 23a below the shelf steps 31, 41.
  • the outlet side flow path 25b is provided on the side closer to the water outlet 23b above the shelf steps 31, 41.
  • the Y-axis direction thickness of the inlet-side channel 25a is smaller than the Y-axis direction thickness of the outlet-side channel 25b.
  • the header part 45 is provided between the inflow part 10a of the flow path space 25 and the water inlet 23a, and extends in the X direction.
  • the header part 45 includes a header part main flow path 45a and a header part throttle flow path 45b.
  • the cross-sectional area in the XY direction of the header portion main flow passage 45a is wider than that of the header portion restriction flow passage 45b. That is, the channel cross-sectional area in the XY direction is orthogonal to the flow of cleaning water flowing from the water inlet 23a to the inflow portion 10a.
  • the flow passage cross-sectional area of the header portion restriction flow passage 45b gradually decreases from the header portion main flow passage 45a toward the inflow portion 10a from the inflow portion 10a.
  • the header throttle channel 45b has a crank shape.
  • the header portion narrowing channel 45b includes a vertical portion 45bb, a horizontal portion 45bc, and a vertical portion 45bd. In the order of the vertical portion 45bb, the horizontal portion 45bc, and the vertical portion 45bd, the cross-sectional areas become smaller (that is, narrower).
  • the flat heater 20 is accommodated in the heater accommodating space 23c of the casing 23 and extends in the vertical direction.
  • the flat heater 20 has a rectangular flat plate shape and includes first and second heat transfer surfaces 20a and 20b on both surfaces.
  • the flat heater 20 includes a ceramic substrate 20k, a resistor pattern 20p, and electrodes (not shown).
  • the temperature of the heat transfer surfaces 20a and 20b is prevented from being locally higher than a predetermined temperature.
  • This predetermined temperature is generally set to 100 ° C. or lower, preferably 80 ° C. or lower, at which boiling occurs in the temperature of the heat transfer surfaces 20a and 20b. Further, the predetermined temperature is appropriately determined depending on the scale concentration of tap water, the required durability time of the heater, and the like.
  • the resistor pattern 20p has a resistor printed on the ceramic substrate 20k.
  • the resistor pattern 20p forms a heating wire (heater wire) and generates heat when energized from the electrodes. As shown in FIG. 7, the heater wire extends long in the X direction and spreads upward in the Z direction while meandering.
  • the heater wire width 20s in the inlet-side channel 25a is narrower than the heater wire width 20s in the outlet-side channel 25b, and the heater wire has a smaller cross-sectional area. The smaller the heater wire width 20s and the smaller the heater wire cross-sectional area, the greater the resistance value of the heater wire. Therefore, the resistance value of the heater wire in the inlet side channel 25a is higher than the resistance value of the heater wire in the outlet side channel 25b.
  • the heat generation density in the resistor pattern 20p in the inlet-side flow path 25a is higher than the heat generation density in the resistor pattern 20p in the outlet-side flow path 25b.
  • the cleaning water enters the header part main flow path 45a of the header part 45. Since the cross-sectional area of the header section throttle flow path 45b is much smaller than the cross-sectional area of the header section main flow path 45a, the resistance from the header section main flow path 45a to the header section throttle flow path 45b is in the X direction of the header section main flow path 45a. Greater than the resistance. Therefore, most of the washing water flows in the X direction of the header part main flow path 45a, and the washing water uniformly fills the header part main flow path 45a. Then, the washing water flows from the header part main flow path 45a to the header part throttle flow path 45b.
  • the flow path cross-sectional area of the header portion narrowing flow path 45b is gradually narrowed, the flow of cleaning water becomes gradually faster. Further, there is no place where air stays in the header throttle channel 45b. For this reason, even if air is mixed in the washing water, the air is carried toward the inflow portion 10a without accumulating.
  • the washing water flows from the inflow portion 10a into the inlet-side flow path 25a, the bubbles rise smoothly by buoyancy along the flow path space 25 in the vertical direction. Further, the bubbles flow to the outflow portion 10b along the top surface of the casing 23 that increases toward the outflow portion 10b. And a bubble is discharged
  • the washing water flows from the inflow portion 10 a into the inlet side flow path 25 a of the flow path space 25.
  • the inlet side channel 25a which is a region where the channel thickness is thin, the flow rate of the cleaning water is fast.
  • the velocity gradient of the boundary layer between each heat transfer surface 20a, 20b of the flat heater 20 and the cleaning water is large, and the heat transfer coefficient between each heat transfer surface 20a, 20b and the cleaning water is large.
  • the heat generation density in the resistor pattern 20p in the inlet-side flow path 25a is high. Therefore, the washing water is heated by the heat transfer surfaces 20a and 20b and becomes high temperature, and its density is reduced. As a result, the washing water rises and flows from the inlet side channel 25a into the outlet side channel 25b.
  • the temperature of each heat transfer surface 20a, 20b tends to increase.
  • the temperature of the cleaning water in the inlet-side flow path 25a is low, the subcool (degree of cooling with respect to the boiling temperature of water) increases and the cleaning water takes a lot of heat from the heat transfer surfaces 20a and 20b.
  • the flow path thickness is thin and the flow rate of the washing water is fast. Therefore, the washing water does not have such a high heat transfer rate that the local boiling phenomenon occurs.
  • the bubbles rise through the outlet side channel 25b having a thick channel in the outlet side channel 25b.
  • the bubbles are discharged from the water outlet 23b.
  • the washing water having such a high temperature flows into the water supply channel 9 from the outlet 23b.
  • the temperature of the wash water is adjusted by a tank (not shown) or the like.
  • the solenoid valve is opened, warm washing water is discharged from the nozzle 7.
  • the header portion restricting passage 45b has a crank shape, the passage in the header portion restricting passage 45b becomes longer. For this reason, even if the cross-sectional area in the header throttle channel 45b is slightly increased, it is possible to ensure channel resistance in the header throttle channel 45b. As a result, the cleaning water can uniformly flow into the header throttle channel 45b over the entire length of the header main channel 45a.
  • a uniform and fast flow of cleaning water along the heat transfer surfaces 20a and 20b is formed in the flow path space 25 by the header throttle flow path 45b.
  • the heat transfer rate between each heat transfer surface 20a, 20b and the washing water is increased.
  • washing water can be heated efficiently.
  • it can suppress that the temperature of each heat-transfer surface 20a, 20b is low, and a scale adheres to each heat-transfer surface 20a, 20b.
  • bubbles generated on the heat transfer surfaces 20a and 20b are easily removed, and the occurrence of local scales and damage to the flat heater 20 due to thermal stress are prevented, and the heat transfer surfaces 20a and 20b and cleaning water
  • stable heat exchange is possible without hindering the heat exchange.
  • the inlet-side channel 25a is close to the header throttle channel 45b and has a small channel thickness. For this reason, in the inlet side flow path 25a, the quick flow from the header part throttle flow path 45b is maintained. Therefore, the velocity gradient in the boundary layer between each heat transfer surface 20a, 20b and the wash water is large, and the heat transfer coefficient due to forced convection between each heat transfer surface 20a, 20b and the wash water is large. The washing water is efficiently heated and the flat heater 20 is prevented from being damaged.
  • the flat heater 20 heats the cleaning water by the heat transfer surfaces 20a and 20b on both the front and back surfaces, there is almost no heat dissipation loss. For this reason, the high heat efficiency of the heat exchanger 10 can be realized and the apparatus can be made compact.
  • the flat heater 20 is suppressed from being heated to such a high temperature that a local boiling phenomenon occurs, and local scale generation is prevented. For this reason, although a heat capacity is small compared with a metal, even if it uses a ceramic for the flat heater 20 if it is easy to break, the crack is prevented and the lifetime of the sanitary washing apparatus 1 is extended.
  • the temperature sensor can appropriately detect the temperature.
  • the bubbles do not become large by discharging the bubbles.
  • a situation is avoided in which large bubbles are attached to the temperature sensor, and the temperature sensor cannot contact the cleaning water due to the large bubbles and cannot detect the temperature of the cleaning water.
  • the forced convection of the washing water and the discharge of the bubbles suppress the scale from adhering to the heat transfer surfaces 20a and 20b. Thereby, in order to avoid the heat transfer failure by a scale, it is not necessary to increase the area of the heat-transfer surfaces 20a and 20b. Therefore, the cost increase of the sanitary washing device 1 can be prevented and the size can be reduced.
  • the sectional area of the header throttle channel 45b is gradually narrower, and the sectional area of the inlet-side channel 25a is narrower than that of the outlet-side channel 25b in the channel space 25. Thereby, even if it does not make flow path thickness thin, the uniform quick flow of the washing water along each heat-transfer surface 20a, 20b is formed.
  • each heat transfer surface 20a, 20b is such that the outlet side flow path 25b is smaller than the inlet side flow path 25a.
  • the flow rate of the washing water is larger in the inlet side channel 25a than in the outlet side channel 25b.
  • the inlet side flow path 25a is higher than the outlet side flow path 25b.
  • the heater wire width 20s in the inlet-side channel 25a is formed to be narrower than the heater wire width 20s in the outlet-side channel 25b.
  • the heater wire width is not limited to 20s.
  • the interval 20h between the heater wires adjacent to each other in the inlet-side channel 25a is narrower than that in the outlet-side channel 25b.
  • the heat generation density in the resistor pattern 20p in the inlet-side flow path 25a is higher than the heat generation density in the resistor pattern 20p in the outlet-side flow path 25b.
  • the header throttle channel 45b has a substantially crank shape, and its channel cross-sectional area is gradually narrowed.
  • the shape of the header throttle channel 45b is not limited to a substantially crank.
  • the header portion restriction channel may be formed by a substantially “ ⁇ ”-shaped cross section formed by two sides of the vertical portion 45bb and the horizontal portion 45bc shown in FIG.
  • it is not limited to what a flow-path cross-sectional area is narrowed in steps.
  • the header restricting flow path may be formed with a triangular cross section whose interval becomes narrower upward. In this case, the flow path cross-sectional area is narrowed gradually.
  • the thickness of the base portions 30 and 40 in the Y direction is changed stepwise by the shelf steps 31 and 41 in the members 21 and 22.
  • two flow paths 25 a and 25 b having different cross-sectional areas are provided in the flow path space 25.
  • each member 21 and 22 may be formed so that the thickness of the base parts 30 and 40 in the Y direction gradually changes.
  • the channel space 25 is provided with one channel whose cross-sectional area gradually changes.
  • the sanitary washing apparatus of the present invention is useful as a sanitary washing apparatus that can secure a necessary flow rate of washing water and prevent failure.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Public Health (AREA)
  • Health & Medical Sciences (AREA)
  • Molecular Biology (AREA)
  • Epidemiology (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Hydrology & Water Resources (AREA)
  • Water Supply & Treatment (AREA)
  • Bidet-Like Cleaning Device And Other Flush Toilet Accessories (AREA)
PCT/JP2012/001522 2011-04-22 2012-03-06 衛生洗浄装置 WO2012144122A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201280000811.0A CN102859086B (zh) 2011-04-22 2012-03-06 卫生清洗装置
KR1020127022666A KR101399717B1 (ko) 2011-04-22 2012-03-06 위생 세정 장치

Applications Claiming Priority (4)

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JP2011-095750 2011-04-22
JP2011-095749 2011-04-22
JP2011095749A JP5786129B2 (ja) 2011-04-22 2011-04-22 熱交換器
JP2011095750 2011-04-22

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CN (1) CN102859086B (ko)
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2784407A1 (en) * 2012-12-17 2014-10-01 Panasonic Corporation Heat exchanger and sanitary cleaning device with same

Families Citing this family (1)

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Publication number Priority date Publication date Assignee Title
JP6155972B2 (ja) * 2013-08-27 2017-07-05 アイシン精機株式会社 熱交換ユニットおよびこれを備える人体局部洗浄装置

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US5245693A (en) * 1991-03-15 1993-09-14 In-Touch Products Co. Parenteral fluid warmer apparatus and disposable cassette utilizing thin, flexible heat-exchange membrane
JPH0988159A (ja) * 1995-09-21 1997-03-31 Toto Ltd 衛生洗浄装置
TW373047B (en) * 1997-04-02 1999-11-01 Matsushita Electric Ind Co Ltd Apparatus for washing human private
JP2000054463A (ja) 1998-08-10 2000-02-22 Toto Ltd 衛生洗浄装置
KR100624568B1 (ko) * 2006-01-02 2006-09-15 주식회사 노비타 세정기용 순간 온수장치
KR100804303B1 (ko) 2007-04-25 2008-02-18 웅진코웨이주식회사 순간 가열 장치
CN201190322Y (zh) * 2008-05-23 2009-02-04 浙江星星便洁宝有限公司 智能座便器瞬间加热装置
KR200453744Y1 (ko) * 2009-01-12 2011-05-27 주식회사 지노아이앤티 비데용 순간 가열 히터 어셈블리

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WO2011027576A1 (ja) * 2009-09-07 2011-03-10 パナソニック株式会社 熱交換器

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2784407A1 (en) * 2012-12-17 2014-10-01 Panasonic Corporation Heat exchanger and sanitary cleaning device with same
EP2784407A4 (en) * 2012-12-17 2015-02-25 Panasonic Corp HEAT EXCHANGER AND SANITARY CLEANING DEVICE HAVING THE SAME

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TWI504370B (zh) 2015-10-21
CN102859086A (zh) 2013-01-02
TW201242561A (en) 2012-11-01
KR101399717B1 (ko) 2014-05-27
CN102859086B (zh) 2015-01-21
KR20120137476A (ko) 2012-12-21

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