WO2011027576A1 - 熱交換器 - Google Patents
熱交換器 Download PDFInfo
- Publication number
- WO2011027576A1 WO2011027576A1 PCT/JP2010/005459 JP2010005459W WO2011027576A1 WO 2011027576 A1 WO2011027576 A1 WO 2011027576A1 JP 2010005459 W JP2010005459 W JP 2010005459W WO 2011027576 A1 WO2011027576 A1 WO 2011027576A1
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- WIPO (PCT)
- Prior art keywords
- heat exchanger
- heater
- flow path
- heat transfer
- flow
- Prior art date
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 344
- 238000010438 heat treatment Methods 0.000 claims abstract description 9
- 230000020169 heat generation Effects 0.000 claims description 44
- 239000000872 buffer Substances 0.000 claims description 43
- 238000011144 upstream manufacturing Methods 0.000 claims description 38
- 239000012530 fluid Substances 0.000 claims description 37
- 238000003756 stirring Methods 0.000 claims description 28
- 239000000919 ceramic Substances 0.000 claims description 23
- 239000000758 substrate Substances 0.000 claims description 7
- 230000007423 decrease Effects 0.000 claims description 6
- 230000000994 depressogenic effect Effects 0.000 claims 1
- 238000004140 cleaning Methods 0.000 abstract description 35
- 238000009835 boiling Methods 0.000 abstract description 22
- 238000005406 washing Methods 0.000 description 63
- 230000015572 biosynthetic process Effects 0.000 description 27
- 238000009826 distribution Methods 0.000 description 9
- 238000013459 approach Methods 0.000 description 6
- 230000001154 acute effect Effects 0.000 description 5
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- 238000005336 cracking Methods 0.000 description 2
- 238000005520 cutting process Methods 0.000 description 2
- 239000003365 glass fiber Substances 0.000 description 2
- 230000002401 inhibitory effect Effects 0.000 description 2
- 230000005855 radiation Effects 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 239000008399 tap water Substances 0.000 description 2
- 235000020679 tap water Nutrition 0.000 description 2
- 239000002699 waste material Substances 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- OYPRJOBELJOOCE-UHFFFAOYSA-N Calcium Chemical compound [Ca] OYPRJOBELJOOCE-UHFFFAOYSA-N 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 238000013019 agitation Methods 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 229910052791 calcium Inorganic materials 0.000 description 1
- 239000011575 calcium Substances 0.000 description 1
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- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
Images
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
-
- 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
- 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
-
- 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
- F24H9/0005—Details for water heaters
- F24H9/001—Guiding means
- F24H9/0015—Guiding means in water channels
-
- H—ELECTRICITY
- H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
- H05B—ELECTRIC HEATING; ELECTRIC LIGHT SOURCES NOT OTHERWISE PROVIDED FOR; CIRCUIT ARRANGEMENTS FOR ELECTRIC LIGHT SOURCES, IN GENERAL
- H05B3/00—Ohmic-resistance heating
- H05B3/10—Heating elements characterised by the composition or nature of the materials or by the arrangement of the conductor
- H05B3/12—Heating elements characterised by the composition or nature of the materials or by the arrangement of the conductor characterised by the composition or nature of the conductive material
- H05B3/14—Heating elements characterised by the composition or nature of the materials or by the arrangement of the conductor characterised by the composition or nature of the conductive material the material being non-metallic
-
- H—ELECTRICITY
- H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
- H05B—ELECTRIC HEATING; ELECTRIC LIGHT SOURCES NOT OTHERWISE PROVIDED FOR; CIRCUIT ARRANGEMENTS FOR ELECTRIC LIGHT SOURCES, IN GENERAL
- H05B3/00—Ohmic-resistance heating
- H05B3/20—Heating elements having extended surface area substantially in a two-dimensional plane, e.g. plate-heater
- H05B3/22—Heating elements having extended surface area substantially in a two-dimensional plane, e.g. plate-heater non-flexible
- H05B3/26—Heating elements having extended surface area substantially in a two-dimensional plane, e.g. plate-heater non-flexible heating conductor mounted on insulating base
- H05B3/265—Heating elements having extended surface area substantially in a two-dimensional plane, e.g. plate-heater non-flexible heating conductor mounted on insulating base the insulating base being an inorganic material, e.g. ceramic
-
- H—ELECTRICITY
- H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
- H05B—ELECTRIC HEATING; ELECTRIC LIGHT SOURCES NOT OTHERWISE PROVIDED FOR; CIRCUIT ARRANGEMENTS FOR ELECTRIC LIGHT SOURCES, IN GENERAL
- H05B3/00—Ohmic-resistance heating
- H05B3/78—Heating arrangements specially adapted for immersion heating
-
- H—ELECTRICITY
- H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
- H05B—ELECTRIC HEATING; ELECTRIC LIGHT SOURCES NOT OTHERWISE PROVIDED FOR; CIRCUIT ARRANGEMENTS FOR ELECTRIC LIGHT SOURCES, IN GENERAL
- H05B2203/00—Aspects relating to Ohmic resistive heating covered by group H05B3/00
- H05B2203/002—Heaters using a particular layout for the resistive material or resistive elements
- H05B2203/003—Heaters using a particular layout for the resistive material or resistive elements using serpentine layout
-
- H—ELECTRICITY
- H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
- H05B—ELECTRIC HEATING; ELECTRIC LIGHT SOURCES NOT OTHERWISE PROVIDED FOR; CIRCUIT ARRANGEMENTS FOR ELECTRIC LIGHT SOURCES, IN GENERAL
- H05B2203/00—Aspects relating to Ohmic resistive heating covered by group H05B3/00
- H05B2203/013—Heaters using resistive films or coatings
-
- H—ELECTRICITY
- H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
- H05B—ELECTRIC HEATING; ELECTRIC LIGHT SOURCES NOT OTHERWISE PROVIDED FOR; CIRCUIT ARRANGEMENTS FOR ELECTRIC LIGHT SOURCES, IN GENERAL
- H05B2203/00—Aspects relating to Ohmic resistive heating covered by group H05B3/00
- H05B2203/037—Heaters with zones of different power density
Definitions
- the present invention relates to an instantaneous heating type heat exchanger used in a sanitary washing apparatus that can wash a human body part with warm water after a stool.
- the sanitary washing device is equipped with a heat exchanger for bringing the washing water to an appropriate temperature when washing the human body part after the toilet with water.
- a heat exchanger for bringing the washing water to an appropriate temperature when washing the human body part after the toilet with water.
- heat exchangers There are various types of heat exchangers, and one of them is a flat plate type as disclosed in Patent Document 1. This is because a flat heater is accommodated vertically in a rectangular parallelepiped casing having a small width dimension, and the two streams flowing upward while meandering horizontally along both heat transfer surfaces of the flat heater. The road is formed. Then, the cleaning water is heated to an appropriate temperature by allowing the cleaning water to flow along each flow path while the flat heater is being driven.
- the water flowing in from the water inlet of the casing is heated on the surface of the flat heater in the flow path from the water inlet to the water outlet.
- the temperature approaches the water outlet, the temperature rises, and a local boiling phenomenon may occur on the surface of the flat heater near the water outlet.
- a so-called scale is generated by the calcium component contained in the washing water in the flow path, and the scale adheres to the surface of the flat heater.
- heat transfer to water is hindered by the scale.
- the surface temperature of the flat heater is locally increased, and the adhesion of the scale is promoted.
- the flow resistance of the deposited scale increases, and the flow rate of the necessary cleaning water may not be ensured. is there.
- the flat heater is a ceramic heater, the flat heater may be cracked or cracked due to thermal strain caused by a partial temperature difference caused by the scale.
- the phenomenon of adhesion of such scales to the heat transfer surface is the most dominant generation factor of the heat transfer surface temperature.
- the heat transfer surface temperature is 100 ° C. or lower, preferably 80 ° C. or lower, at which boiling occurs.
- the required heat transfer surface temperature is appropriately determined according to the scale concentration of tap water and the required durability of the heater. If a part of the heat transfer surface temperature exceeds the required temperature, scale will adhere to that part and cause heat transfer obstruction, so this must be avoided. In order to avoid this, it is sufficient to simply increase the area of the heat transfer surface, but this is not preferable because it increases the cost of the heat exchanger.
- the flat plate heater is designed so that the local temperature distribution on the heat transfer surface is substantially uniform over the entire heat transfer surface. It is necessary to configure the heat exchanger to set a local distribution of watt density or a local heat transfer coefficient distribution of the heat exchanger.
- the heat transfer rate is improved to suppress the generation of bubbles, or the generated bubbles are quickly discharged from the outlet to the outside, and the heat transfer rate is further increased. It is conceivable to reduce the heat transfer area by improving it.
- the width of the flow path is set very narrow. It is necessary to secure the flow velocity.
- the maximum value of this flow rate is set to about 500 cc / min.
- a flow path formed between the heat transfer surface of the flat plate heater In order to further increase the flow rate of the heat exchanger with respect to this flow rate value, a flow path formed between the heat transfer surface of the flat plate heater.
- an object of the present invention is configured such that the flat heater is configured so that the watt density is lower on the outlet side having a relatively high water temperature than on the inlet side having a low water temperature.
- an object of the present invention is to provide a long-life heat exchanger capable of suppressing the generation and adhesion of scale by making the heat transfer surface temperature uniform and suppressing the maximum surface temperature of the heater.
- an object of the present invention is to provide a heat exchanger that suppresses the generation of bubbles generated inside and can quickly guide the generated bubbles to a water outlet.
- a heat exchanger includes a casing having a water inlet and a water outlet, a heater disposed in the casing and having a surface that forms a heat transfer surface, and formed in the heater, and flows from the water inlet.
- a flow path space that guides the fluid to reach the water outlet while heat exchange with the heat transfer surface of the heater, and the heater has a heat generation density in a portion near the water outlet at the water inlet. It is formed to be smaller than the heat generation density in the near portion (claim 1).
- the fluid (for example, washing water) flowing in from the water inlet of the casing is heated by the heat transfer surface of the heater surface while flowing through the flow path, and the temperature of the fluid gradually increases as it approaches the water outlet.
- the surface temperature of the heater near the water inlet tends to become high due to the high heat generation density of the heater, but a lot of heat is taken away by the low-temperature fluid that has not yet been heated (that is, the subcool value is large). Therefore, the temperature is not high enough to cause local boiling.
- the surface temperature of the heater near the water outlet tends to be higher than that near the water inlet because the fluid in contact with the heater surface has already been heated.
- the heater is formed so that the heat generation density on the side near the water outlet is smaller than the heat generation density on the side near the water inlet. Therefore, the temperature is not high enough to cause local boiling.
- the heater is formed such that the heat generation density on the side close to the water outlet is smaller than the heat generation density on the side close to the water inlet, so that the boundary between the heater near the water outlet and the water where the temperature of the fluid is high becomes higher. Also in terms of surface, it is possible to prevent a high temperature at which a local boiling phenomenon occurs, prevent scale formation and adhesion, and provide a long-life heat exchanger. On the other hand, the heat density of the heater is increased on the inlet side where the temperature of the fluid is relatively low and the flow velocity tends to be higher than that of the outlet, so heat exchange in the vicinity of the inlet Efficiency can be improved.
- the heater is a flat plate heater arranged substantially parallel to the vertical direction, and two main surfaces of the front and back surfaces form the heat transfer surface,
- the flow path space may be formed from the lower water inlet to the upper water outlet along each of the heat transfer surfaces on the front and back of the flat heater (Claim 2).
- the temperature close to the water outlet of the flat heater is the highest temperature, and a scale is first generated in this area. Is done.
- the heat generation density distribution of the flat heater is set so that the vicinity of the water outlet is smaller than the vicinity of the water inlet, and as a result, the heat flux of the heat exchanger is high at the portion where the heat generation density of the heater is large, Since the heat generation density is low at a location where the heat generation density is small, the heat transfer surface temperature is made uniform, and the temperature does not rise locally and scale does not adhere to it.
- the heat of the flat heater is transferred to the washing water flowing in contact with both sides of the front and back, and heat exchange with high thermal efficiency with almost no waste of heat radiation loss can be achieved. Since both sides can be used as heat transfer area, it can be made compact and compact.
- the heater is a ceramic heater comprising a ceramic base, a heating resistor formed by pattern printing a resistor on the ceramic base, and an electrode, and the printing
- the line width of the pattern may be formed so that the portion near the water outlet is thicker than the portion near the water inlet (Claim 3).
- the heater is a ceramic heater comprising a ceramic base, a heating resistor formed by pattern printing a resistor on the ceramic base, and an electrode, and the printing
- the gap between the lines of the pattern may be formed wider in the portion near the water outlet than in the portion near the water inlet (Claim 4).
- the side near the water inlet having a narrow gap between the lines of the print pattern generates a large amount of heat (that is, the heat generation density is large), and the gap between the lines of the print pattern is close to a wide outlet.
- the side becomes a ceramic heater that generates a small amount of heat (that is, a small heat generation density). Therefore, for the same reason as described above, scale generation and adhesion can be prevented, and cracking of the ceramic heater can be prevented, and a long-life heat exchanger can be realized.
- the flow path space includes an upstream space including an opening of the water inlet and a downstream space including an opening of the water outlet, and the upstream space.
- a throttle channel having a smaller flow cross-sectional area than that of the other part may be provided between the downstream space and the downstream space (Claim 5).
- the flow path space may be formed symmetrically on one heat transfer surface side and the other heat transfer surface side of the flat heater. ).
- the two flow passage spaces are symmetrically formed on one heat transfer surface side and the other heat transfer surface side of the flat heater” means “two flow passage spaces”.
- a flat heater is disposed between the spaces, and the positional relationship between the two flow passage spaces is substantially symmetrical with respect to the heat transfer surface (at least one of the two) of the flat heater.
- the heat transfer surfaces first heat transfer surface 20a or second heat transfer surface 20b shown in FIGS. 2 and 3 to be described later are opposed to each other so as to have a plane-symmetrical positional relationship.
- the positional relationship between the two flow path spaces 25, 25 arranged can be given.
- the downstream space may have a larger capacity than the upstream space (Claim 7).
- the fluid flow rate can be increased in the downstream space with a large capacity, so that the heat transfer rate can be further improved.
- the throttle flow path is a horizontal throttle flow extending in a substantially horizontal direction from the vicinity of the water inlet so as to allow fluid to flow upward toward the downstream space. You may have a path (Claim 8).
- the fluid passing through the horizontal throttle channel is heated by the heater and is directed upward in the same direction as the relatively hot fluid rises by natural convection.
- the flow rate can be further improved by directing the fluid that has passed through the horizontal throttle channel upward in the same manner as natural convection.
- the throttle channel has an end portion that is separated from the water inlet in the horizontal throttle channel so that the fluid flows further in the horizontal direction toward the downstream space.
- a vertical throttle channel extending substantially vertically upward may be included (claim 9).
- the throttle channel may have a slit shape, and the throttle channel may have a widened portion having a larger opening width than other portions. ).
- a stirring wall for stirring the fluid is extended substantially vertically along the flat heater in the downstream space, and the stirring wall is horizontally You may have the shape which wavy in the direction (Claim 11).
- the fluid in the downstream space can be further stirred by the stirring wall to improve the heat transfer coefficient. Further, since the stirring wall is extended in the vertical direction, the generated bubbles are not hindered from rising due to their buoyancy, and can be quickly moved to the water outlet and discharged.
- the downstream space may be provided with a buffer wall extending in a substantially horizontal direction along the flat heater (Claim 12).
- the fluid flowing through the downstream space is once blocked before each buffer wall and diffuses when passing through a narrow gap between the buffer wall and the flat heater. Therefore, the fluid can be agitated to improve the heat transfer coefficient.
- a plurality of the buffer walls are arranged in the vertical direction, and the buffer walls are notched so that the positions of the buffer walls are different from each other in the vertical direction when viewed in plan.
- a portion may be formed (claim 13).
- the heat exchanger according to the present invention includes a pair of flow path forming members disposed with the flat plate heater interposed therebetween, and the flow path forming member has a flat plate shape arranged to face the flat plate heater.
- a path may be configured (claim 14).
- a heat exchanger having a throttle channel can be realized with a relatively simple configuration.
- the heater is a flat plate heater arranged substantially parallel to the vertical direction, and two main surfaces of the front and back surfaces form the heat transfer surface,
- the flow path space may be formed in a meandering flow path extending from the lower water inlet to the upper water outlet along each of the heat transfer surfaces on the front and back of the flat heater. Item 15).
- the heat of the flat heater is transferred to the washing water flowing in contact with both sides of the front and back, and heat exchange with high thermal efficiency with almost no waste of heat radiation loss can be achieved. Since both sides can be used as a heat transfer area, it can be made compact and compact.
- the flow path length can be increased by the meandering flow path and the flow velocity is increased, the thickness of the layer (temperature boundary layer) that is substantially transferred from the heater surface in the fluid becomes thinner. Accordingly, the heat transfer efficiency is improved and the temperature of the heater surface is further lowered, so that the local boiling phenomenon can be further suppressed and the effect of preventing the generation and adhesion of scale can be further enhanced.
- the meandering flow path is defined by a plurality of walls extending in a substantially horizontal direction and arranged in parallel in the vertical direction, and the fluid is substantially passed from the water inlet to the water outlet.
- the flow path leading in one direction in the horizontal direction and the flow path leading in the other direction are alternately provided from the lower side to the upper side, and the wall portion in the middle in the longitudinal direction is adjacent to the upper and lower sides.
- a bypass path in the vertical direction communicating with the flow path may be formed (claim 16).
- the bubbles are discharged to the water outlet through the vertical bypass formed in the meandering flow path. And promptly. That is, since the cross-sectional area of the flow path is reduced by the meandering flow path, the flow rate of the cleaning water can be increased and made uniform. Further, as described above, since the heater has a heat generation density near the water outlet lower than that near the water inlet, the heat transfer surface may cause a local boiling phenomenon of the washing water. High temperature is suppressed, and the generation of bubbles is also suppressed.
- the generated bubbles are passed through the bypass path with a channel length shorter than the total length of the meandering channel. It is possible to move quickly to the water outlet. As a result, the flow resistance on one heat transfer surface side of the heater is biased and increased compared to the other due to bubbles, or only the temperature of one heat transfer surface of the heater is greatly increased compared to the other. Can be prevented. Thereby, the local boiling phenomenon that causes generation and adhesion of scale can be further suppressed. Moreover, since the bubble generated on the surface of the heater is quickly discharged from the water outlet through the bypass as described above, the bubble can be prevented from growing greatly. Accordingly, it is possible to prevent bubbles from growing greatly and inhibiting the operation of the thermistor near the water outlet.
- the said meandering flow path and the said bypass path may be formed symmetrically by the one heat-transfer surface side of the said flat heater, and the other heat-transfer surface side. (Claim 17).
- the two meandering channels are formed symmetrically on one heat transfer surface side and the other heat transfer surface side of the flat heater” means “two meandering channels”
- a flat heater is disposed between the flow paths, and the positional relationship between the two meandering flow paths is substantially symmetrical with respect to the heat transfer surface (at least one of the two) of the flat heater as a symmetry plane. It is said that they are arranged so as to face each other.
- the heat transfer surfaces first heat transfer surface 120a or second heat transfer surface 120b shown in FIG. 15 and FIG.
- the positional relationship between the two meandering channels (meandering channel 135 and meandering channel 145).
- the two bypass passages are formed symmetrically on one heat transfer surface side and the other heat transfer surface side of the flat heater” means “a flat plate shape between the two bypass passages”.
- the heaters are arranged, and the two serpentine flow paths are arranged so as to face each other so that the heat transfer surfaces (at least one of the two) of the flat plate heater are symmetrical with respect to the plane of symmetry. State.
- bypass passages formed in the plurality of wall portions may be provided so that their positions when viewed in plan are substantially coincident (claim 18).
- the heat exchanger according to the present invention includes a pair of flow path forming members disposed with the flat plate heater interposed therebetween, and the flow path forming member has a flat plate shape facing the flat plate heater. And a plurality of ribs that project from the surface of the base portion facing the flat heater and form the wall portion. Alternatively, the rib may have a notch that is recessed to form the bypass path (Claim 19).
- a bypass path can be formed by cutting out a part of the rib tip.
- the notch portion of the rib may have a tapered shape in plan view so that the notch width decreases as the notch depth increases. ).
- the notch portion of the rib may have an arc shape in plan view so that the notch depth of the center portion of the notch width is increased. ).
- the notch width of the notch portion may be larger in the rib provided in the upper side than the rib provided in the lower side (claim). Item 22).
- the notch width of the notch part is reduced to improve the flow velocity. Can be planned.
- the notch width of the notch part can be increased so that the bubbles can pass through with certainty.
- the notched portion is not formed in the rib provided relatively below, and the notched portion is formed relative to the rib provided relatively above. It may be formed (claim 23).
- the flow velocity is further improved without providing a notch in the lower part where bubbles are not easily generated, while the notch part is provided in the upper part where bubbles are likely to be generated to ensure the bubbles. Can be passed through.
- the present invention it is possible to suppress the generation of bubbles and prevent the generation and adhesion of scales while suppressing the occurrence of high-temperature bubbles that cause a local boiling phenomenon and improving the heat transfer coefficient.
- a long-life heat exchanger can be provided.
- produced quickly to a water outlet is provided.
- FIG. 3 is a cross-sectional view taken along line BB of the heat exchanger shown in FIG. It is a top view which shows the example of a pattern of the resistor formed in the flat heater of the heat exchanger shown in FIG. It is a top view which shows another example of a pattern of the resistor formed in the flat heater of the heat exchanger shown in FIG.
- FIG. 4B is a cross-sectional view taken along line BB of the heat exchanger
- 5C is a cross-sectional view taken along line CC of the heat exchanger. It is drawing which shows the structure which concerns on Embodiment 6 of a heat exchanger, (a) is when the heat exchanger of the state which removed the 2nd flow path formation member was seen from the base surface side of the 1st flow path formation member. A plan view showing the configuration, (b) is a cross-sectional view of the heat exchanger taken along line BB. It is drawing which shows the structure which concerns on Embodiment 7 of a heat exchanger, (a) is when the heat exchanger of the state which removed the 2nd flow path formation member was seen from the base surface side of the 1st flow path formation member.
- FIG. 1 A plan view showing the configuration, (b) is a cross-sectional view of the heat exchanger taken along line BB. It is drawing which shows the modification of the heat exchanger demonstrated in Embodiment 1, and saw the heat exchanger of the state which removed the 2nd flow path formation member and the flat heater from the base surface side of the 1st flow path formation member. The structure of when is shown. It is drawing which shows the structure of the heat exchanger which concerns on Embodiment 8, (a) is a front view which shows an external appearance structure, (b) is sectional drawing in the BB line.
- FIG. 16 is an enlarged view of a portion XVIIIb in FIG. 15 to show the configuration when viewed along the X direction. It is drawing which shows the flow of the washing water and bubbles in the heat exchanger which concerns on Embodiment 8, and is a top view which shows a structure when it sees from the base surface side of a 1st flow-path formation member. In Embodiment 9, it is an enlarged view when a notch part is seen along a Z direction to show other composition of a notch part, and (a) is an enlarged view showing the deepest part of a notch part being a taper shape.
- (B) is an enlarged view in which the deepest part of a notch part has an arcuate shape
- (c) is an enlarged view in which the deepest part has an inclined surface. It is drawing which shows the structure of the heat exchanger which concerns on Embodiment 10, and is a top view which shows a structure when it sees from the base surface side of a 1st flow-path formation member. It is drawing which shows the structure of the heat exchanger which concerns on Embodiment 11, and is a top view which shows a structure when it sees from the base surface side of a 1st flow-path formation member.
- FIG. 1 is an external perspective view showing a sanitary washing apparatus including a heat exchanger according to an embodiment of the present invention.
- the sanitary washing device 1 is disposed on the upper surface of the toilet 2, and includes a main body 3, a toilet seat 4, a toilet lid 5, an operation unit 6, and the like.
- the main body 3 is disposed on the rear side (back side as viewed from the seated user) of the toilet seat 4, and in a horizontally long and hollow housing 3a, a cleaning unit, a drying unit (not shown), and
- a heat exchanger 10 illustrated by a broken line according to the present embodiment is accommodated.
- tap water fluid, liquid, washing water
- a water supply facility attached to the building where the toilet 2 is installed, and is heated to an appropriate temperature inside.
- the cleaning unit is driven, and cleaning water is jetted from the nozzles of the cleaning unit to the human body part in a shower shape. ing.
- FIGS. 2 and 3 are drawings showing the configuration of the heat exchanger 10 (10A), FIG. 2 is a front view showing the external configuration, and FIG. 3 is a sectional view taken along line BB of FIG. Yes.
- the heat exchanger 10A is configured to have a flat plate-like appearance having a small thickness and a rectangular shape when viewed from the front, and as shown in FIG. 3, a flat plate having a rectangular flat plate shape.
- first flow path forming member 21 disposed opposite to one surface (first heat transfer surface) 20a
- second flow path disposed opposite to the other surface (second heat transfer surface) 20b
- a forming member 22 and a casing 23 that accommodates these members and has a water inlet 23a and a water outlet 23b are provided.
- the flat heater 20 is made of ceramic
- the first flow path forming member 21 and the second flow path forming member 22 are made of reinforced ABS resin in which glass fiber is compounded with ABS resin.
- the vertical direction is the Z direction
- the direction perpendicular to this and parallel to the heat transfer surface of the flat plate heater 20 is the X direction
- the direction perpendicular to both of these two directions is taken as the Y direction.
- the first flow path forming member 21 includes a rectangular flat base portion 30 that faces the first heat transfer surface 20 a, and a surface (base) that faces the first heat transfer surface 20 a in the base portion 30. Surface) 30a and a single rib 31 projecting from the surface 30a.
- the second flow path forming member 22 has a rectangular flat plate-like base portion 40 facing the second heat transfer surface 20b, and a surface (base surface) 40a facing the second heat transfer surface 20b in the base portion 40. And one rib 41 projecting from the head.
- a wall-shaped flange portion 32 is provided around the periphery of the base portion 30 of the first flow path forming member 21, and the flange portion 32 is directed toward the second flow path forming member 22. It is extended by a predetermined dimension.
- An engaging groove 33 that circulates along the flange portion 32 is formed at the distal end portion of the flange portion 32.
- a wall-like flange portion 42 is also provided around the periphery of the base portion 40 of the second flow path forming member 22, and the flange portion 42 is directed away from the first flow path forming member 21. It is extended by a predetermined dimension.
- the front end portion of the flange portion 42 is folded back toward the first flow path forming member 21, and an engagement protrusion 43 that circulates along the flange portion 42 is formed at the end portion.
- the first flow path forming member 21 is externally attached to the second flow path forming member 22 such that the base surface 30a faces the base surface 40a of the second flow path forming member 22. More specifically, the flange portion 32 of the first flow path forming member 21 is externally fitted to the flange portion 42 of the second flow path forming member 22, and the second flow is inserted into the engagement groove 33 of the first flow path forming member 21.
- the engagement protrusion 43 of the path forming member 22 is fitted (for example, the engagement protrusion 43 is fixed to the engagement groove 33 by ultrasonic welding). Thereby, the first flow path forming member 21 and the second flow path forming member 22 are joined in a liquid-tight manner, and a flow path space 25 is formed inside.
- a water inlet 23a is provided at the lower end of the casing 23 in the X direction, and a water outlet 23b is provided at the upper end of the casing 23. As shown in FIG. 3, both the water inlet 23 a and the water outlet 23 b communicate with the flow path space 25.
- FIG. 4 is a plan view showing a pattern example of a resistor formed on the flat heater 20 of the heat exchanger shown in FIG.
- the flat heater 20 has a structure in which a resistor (heater wire) pattern 20p is printed on a ceramic substrate 20k.
- the resistor pattern 20p is configured such that the heater line width 20s is narrow at a portion near the water inlet 23a of the flat heater 20 and the heater line width 20s is thick at a portion near the water outlet 23b. .
- the heater line width 20s becomes narrower and closer to the water inlet 23a of the flat heater 20, and the resistance value becomes higher, and the heater line width 20s becomes thicker as it approaches the water outlet 23b.
- the resistance value becomes lower.
- the flat heater 20 is formed so that the heat generation density in the portion near the water outlet 23b is lower than the heat generation density in the portion near the water inlet 23a.
- FIG. 5 is a plan view showing another pattern example of the resistor formed on the flat heater 20 of the heat exchanger shown in FIG.
- the flat heater 20 has a structure in which the resistor (heater wire) pattern 20p is printed on the ceramic substrate 20k.
- the adjacent heater wire interval 20h is narrow in the portion of the flat heater 20 near the water inlet 23a, and the heater wire interval is close to the outlet 23b. 20h is configured to be wide.
- the flat heater 20 is formed so that the heater line interval 20h becomes narrower and the heat generation density becomes higher as it gets closer to the water inlet 23a, and the heater line interval 20h becomes wider and the heat generation density becomes lower as it gets closer to the water outlet 23b. Has been.
- the configuration including the resistor pattern 20p related to the flat heater 20 shown in FIGS. 4 and 5 is the flat plate shape of the heat exchanger described in the second to seventh embodiments described later in addition to the first embodiment. The same applies to the heater 20 and the flat heater 120 of the heat exchanger described in the eighth to eleventh embodiments.
- FIG. 6 is a view when the heat exchanger 10A is disassembled.
- FIG. 6A shows the heat exchanger 10A in a state where the second flow path forming member 22 and the flat plate heater 20 are removed.
- a single rib 31 extending along the substantially horizontal direction (X direction) is disposed on the base surface 30 a of the base portion 30 of the first flow path forming member 21.
- the X-direction one end 31a of the rib 31 is positioned in the vicinity of the upper side of the flow passage space side opening of the water inlet 23a, and is in contact with the inner wall surface of the X-direction one end side portion of the flange portion 32.
- the rib 31 extends from the one end portion 31a in the X direction on the base surface 30a along the X direction, and the other end portion 31b in the X direction abuts against the inner wall surface of the other end portion in the X direction of the flange portion 32. ing.
- a single rib 41 extending along the substantially horizontal direction (X direction) is also disposed on the base surface 40a of the base portion 40 of the second flow path forming member 22.
- the first flow path forming member 21 and the second flow path forming member 22 are symmetric with respect to the ribs 31 and 41. That is, the rib 41 also has the X direction one end 41a near the upper side of the water inlet 23a, and the flange 32 has one end side in the X direction when the flow path forming members 21 and 22 are joined. It is located at a location that contacts the inner wall surface of the portion.
- the rib 41 extends from the one end portion 41a in the X direction on the base surface 40a along the X direction.
- the other end portion 41b in the X direction has the flange portion 32 when the flow path forming members 21 and 22 are joined. It is located in the location contact
- the flow path space 25 is divided into a relatively lower upstream space 25a and an upper downstream space 25b by the ribs 31 and 41 as described above.
- the upstream space 25a has a water inlet 23a
- the downstream space 25b has a water outlet 23b
- the downstream space 25b has a larger capacity than the upstream space 25a. have.
- the flow path forming members 21 and 22 are joined to each other with the flat heater 20 sandwiched therebetween, so that the upstream space 25a and the downstream space 25b have their respective thickness directions (Y direction). ), And is divided into a first heat transfer surface 20a side and a second heat transfer surface 20b side (see FIG. 3).
- FIG. 7 shows the configuration when the vicinity of the ribs 31 and 41 of the heat exchanger 10A after assembly is viewed along the X direction in order to show the configuration of the throttle channels 37 and 47.
- FIG. 3 is an enlarged view of the third portion VIIa, and (b) shows a modification of the throttle channels 37 and 47.
- the ribs 31 and 41 each have a flat heater whose end surface 50 (the end in the Y direction on the side close to the flat heater 20) has an end surface 50. It is not parallel to the 20 heat transfer surfaces 20a, 20b. That is, the end surfaces 50 of the ribs 31 and 41 are inclined surfaces that open upward. More specifically, the upper surfaces of the ribs 31 and 41 have a predetermined angle A and are separated from the heat transfer surfaces 20a and 20b compared to the lower portions. It is an inclined surface. Therefore, the tip portion of the rib 31 is formed in a triangular shape so that the lower portion has a top portion 51 protruding in an acute angle shape. The tips of the top portions 51 of the ribs 31 and 41 are set so as to be separated from the heat transfer surfaces 20a and 20b of the flat heater 20 by a predetermined dimension D1.
- slit-shaped throttle channels 37 and 47 having an opening width dimension D ⁇ b> 1 are formed between the ribs 31 and 41 and the heat transfer surfaces 20 a and 20 b of the flat heater 20.
- the upstream space 25a of the heat exchanger 10A according to the present embodiment is a closed space except for the water inlet 23a and the throttle channels 37 and 47, and the downstream space 25b is a water outlet 23b.
- the closed space except for the throttle channels 37 and 47 is a closed space. Therefore, the upstream space 25a and the downstream space 25b are configured to communicate with each other only by the throttle channels 37 and 47 having a narrow opening width dimension D1.
- washing water is introduced from the water inlet 23a into the flow path space 25 of the heat exchanger 10A, and this washing water enters the upstream space 25a.
- the upstream space 25a has a pressure equalizing function for making the flow of the washing water flowing into the downstream space 25b uniform.
- the upstream space 25a is a closed space except for the water inlet 23a and the narrow throttle channels 37 and 47, a predetermined relatively high internal pressure is generated in the internal wash water. Therefore, when such high-pressure washing water enters the downstream space 25b through the throttle channels 37 and 47, the flow rate of the washing water in the downstream space 25b can be increased.
- the flow rate pattern of the washing water in the downstream space 25b is schematically shown by reference numerals V1, V2, and V3 in FIG.
- the washing water immediately after passing through the throttle channels 37 and 47 has a high flow velocity especially on the side close to the surface of the flat heater 20, and has a flow velocity pattern as indicated by reference numeral V1.
- the flow velocity pattern that is gradually averaged as indicated by reference numerals V2 and V3 (the portion with the fastest flow velocity is located at an intermediate position between both the second heat transfer surface 20b and the base surface 40a). (Flow velocity pattern approaching).
- the flow velocity pattern is the same as described above.
- the flow rate pattern of the washing water immediately after passing through the throttle channels 37 and 47 becomes a flow rate pattern as indicated by reference numeral V1, so that the heat transfer rate from the heat transfer surfaces 20a and 20b of the flat plate heaters. Can be improved. Furthermore, as the flow velocity near the heater surface gradually decreases from the water inlet 23a toward the water outlet 23b, the heat transfer coefficient is high on the water inlet 23a side and the heat transfer coefficient is low on the water outlet 23b side. Become.
- the flow by the forced convection in the downstream space 25b (that is, the flow upward through the throttle channels 37 and 47 to the downstream space 25b) is the washing water generated by heating the flat heater 20. It is the same direction as the flow by natural convection, and the heat transfer coefficient can be further increased by increasing the flow velocity of these two flows.
- the tip portions of the ribs 31 and 41 have a top portion 51 whose lower portion protrudes in an acute angle shape, and therefore immediately after passing through the throttle channels 37 and 47.
- This water flow collides with the wash water in the downstream space 25b and generates turbulent flow.
- the turbulent flow of the wash water in the downstream space 25b can be made to stir the wash water, and the heat transfer coefficient from the heat transfer surfaces 20a and 20b of the flat heater 20 can be improved. Can be achieved.
- the flow rate can be further increased to increase the heat transfer coefficient.
- the flat heater 20 is formed such that the heat generation density in the portion near the water outlet 23b is lower than the heat generation density in the portion near the water inlet 23a, and the water inlet In the portion close to 23 a, the flow rate of the cleaning water flowing while contacting the heat transfer surfaces 20 a and 20 b of the flat heater 20 is increased by the throttle channels 37 and 47 provided in the channel space 25.
- a lot of heat can be efficiently transferred to the wash water at a portion near the water inlet 23a through which the relatively low temperature wash water flows, and an excessive amount at the portion near the water outlet 23b through which the relatively high temperature wash water flows. It is possible to prevent heat from being transferred to the washing water.
- the heat generation distribution of the flat heater 20 and the heat exchange efficiency distribution can be matched, and the local boiling phenomenon on the surface of the flat heater 20 and the generation of bubbles due to this phenomenon are suppressed.
- downstream space 25b including the water outlet 23b is formed as a relatively wide space without a structure that becomes a barrier, even if bubbles are generated, this is raised together with the water flow while rising due to buoyancy. It does not obstruct going to the water outlet 23b. Therefore, even when bubbles are generated, they can be quickly discharged to the outside.
- 10 A of heat exchangers which concern on this Embodiment can aim at the improvement of a heat transfer rate, implement
- the end surface 54 at the tip is the heat transfer surface 20 a of the flat heater 20.
- 20b is not parallel. That is, the end surfaces 54 of the ribs 31 and 41 are inclined surfaces that open downward. More specifically, the ribs 31 and 41 have a predetermined angle A and the lower portion is separated from the heat transfer surfaces 20a and 20b compared to the upper portion. It is an inclined surface. Therefore, the tip end portion of the rib 31 is formed in a triangular shape so that the upper portion has a top portion 55 protruding in an acute angle shape.
- the tips of the top portions 55 of the ribs 31 and 41 are set so as to be separated from the heat transfer surfaces 20a and 20b of the flat heater 20 by a predetermined dimension D1.
- slit-shaped throttle channels 38 and 48 having an opening width dimension D1 are formed between the ribs 31 and 41 and the heat transfer surfaces 20a and 20b of the flat heater 20.
- the present embodiment is formed such that the heat generation density in the portion near the water outlet 23b of the flat heater 20 is smaller than the heat generation density in the portion near the water inlet 23a.
- the flow path space 25 includes an upstream space 25a including an opening of the water inlet 23a and a downstream space 25b including an opening of the water outlet 23b.
- the upstream space 25a and the downstream space 25b In the middle, throttle channels 37 and 47 having a smaller cross-sectional area of flow than other portions are provided.
- the surface temperature of the flat heater 20 near the water inlet 23a tends to become higher due to the relatively high heat generation density, but much heat is taken away by the low-temperature washing water that has not yet been heated. Therefore, the temperature is not high enough to cause local boiling.
- the flow rate of the wash water from the upstream space 25a toward the downstream space 25b increases through the throttle channels 37 and 47. Therefore, particularly in the downstream space 25b, it is possible to improve the heat transfer rate from the flat heater 20 to the washing water and to optimize the distribution of the heat transfer rate, and to promptly move the air bubbles to the water outlet 23b. Can be guided.
- the cleaning water that contacts the surface of the flat heater 20 has already been heated to a certain degree and has become a high temperature. Therefore, in this portion, the surface temperature of the flat plate heater 20 is kept constant. If so, the amount of heat lost to the wash water is reduced. However, since the heat generation density of the flat-plate heater 20 in the portion is formed so as to be smaller than the heat generation density in the portion close to the water inlet 23a, the temperature is not high enough to cause a local boiling phenomenon.
- the throttle channels 37 and 47 having a smaller flow cross-sectional area than the other portions are provided between the upstream space 25a and the downstream space 25b, and the flat heater 20 is a portion close to the water outlet 23b.
- the heat generation density is smaller than the heat generation density of the portion close to the water inlet 23a.
- FIG. 8 is a drawing showing another configuration of the heat exchanger 10, and FIG. 8A shows the heat exchanger 10 with the second flow path forming member 22 removed and the base surface 30 a side of the first flow path forming member 21.
- (B) has shown an example of the flow of washing water.
- the heat exchanger 10 (10B) has ribs 61 extending in the horizontal direction from the vicinity of the water inlet 23a, and the ribs 61 are bent in the middle and upward in the vertical direction. It has an extended configuration.
- the X-direction one end 61a of the rib 61 is located near the upper part of the flow passage space side opening of the water inlet 23a and is in contact with the inner wall surface of the X-direction one end side portion of the flange portion 32.
- the rib 61 extends from the one end portion 61a in the X direction on the base surface 30a along the X direction, and the other end portion 61b in the X direction has a predetermined distance from the inner wall surface of the other end portion in the X direction of the flange portion 32. Is located only apart.
- the rib 61 is bent at the other end portion 61 b and is directed upward, and the upper end portion 61 c is in contact with the inner wall surface of the upper portion of the flange portion 32.
- the rib space 61 divides the flow path space 25 into a substantially L-shaped upstream space 25a and a rectangular downstream space 25b.
- the upstream space 25a is defined by a portion (horizontal space) 62 defined by a portion between the end portions 61a and 61b of the rib 61 and extending in the horizontal direction, and a portion between the end portions 61b and 61c of the rib 61.
- a portion (vertical space) 63 extending in the vertical direction, the shape is substantially L-shaped as described above.
- the second flow path forming member 22 also has a rib symmetrical to the rib 61.
- throttle channels (horizontal throttle channels and vertical throttle channels) 65 having a flow cross-sectional area smaller than the flow cross-sectional areas of the upstream space 25a and the downstream space 25b are formed. . That is, by combining each flow path forming member 21, 22 and the flat heater 20, a slit shape is formed between the portion between the ends 61 a, 61 b of the rib 61 and the first heat transfer surface 20 a of the flat heater 20.
- the horizontal throttle channel 65a is formed.
- a slit-like vertical throttle channel 65b is also formed between the end 61b, 61c of the rib 61 and the first heat transfer surface 20a.
- the height of the rib 61 from the base surface 30a is constant over the entire length between the end portions 61a to 61c, and the base surface 30a and the first heat transfer surface 20a are parallel to each other. Is arranged. Accordingly, the horizontal throttle channel 65a and the vertical throttle channel 65b have substantially the same opening width.
- the horizontal space 62 passes through the horizontal throttle channel 65a as described in the first embodiment.
- a high-speed water flow enters the downstream space 25b and flows vertically upward.
- a high-speed water flow enters the downstream space 25b from the vertical space 63 through the vertical throttle channel 65b, and this water flow flows in the horizontal direction. Therefore, in the downstream space 25b, since the water flow vertically upward and the water flow in the horizontal direction coexist, the turbulent flow is generated, the washing water is stirred, and the heat transfer rate can be improved.
- the heat generation density of the portion near the water outlet 23b of the flat heater 20 is formed to be smaller than the heat generation density of the portion near the water inlet 23a, or if bubbles are generated, this is quickly removed from the water outlet 23b. As in the case of the first embodiment, it can be discharged.
- FIG. 9 is a drawing showing still another configuration of the heat exchanger 10.
- FIG. 9A shows the heat exchanger 10 with the second flow path forming member 22 removed and the base surface 30 a of the first flow path forming member 21. The structure when viewed from the side is shown, and (b) shows an example of the flow of washing water.
- the heat exchanger 10 (10C) has the straight and horizontal ribs 31 similar to those shown in the first embodiment, while in the downstream space 25b, A plurality of stirring walls 67 having a corrugated shape are provided.
- the base surface 30a of the first flow path forming member 21 is provided with a rib 31 extending in the horizontal direction from the inner wall surface on one end side in the X direction to the inner wall surface on the other end side of the flange portion 32.
- the rib 31 has the throttle channel 37 configured in the same manner as in the first embodiment.
- a stirring wall 67 extends upward from the rib 31 along the base surface 30a.
- the stirring wall 67 extends upward while being curved in an arc shape like a sine waveform having a predetermined amplitude in the X direction.
- a plurality of such stirring walls 67 are arranged in parallel in the X direction at substantially equal intervals (six in this embodiment).
- the height dimension of the stirring wall 67 from the base surface 30 a is set to be substantially the same as the height dimension of the rib 31 or slightly lower than the height dimension of the rib 31. Further, the two adjacent agitation walls 67 are spaced apart so as not to overlap each other when viewed in plan along the Z direction. That is, a route that can move linearly from below to above is secured between two adjacent stirring walls 67 without moving horizontally so as to avoid both stirring walls 67.
- the water flow that has flowed into the downstream space 25b from the throttle channel 37 at high speed is stirred by colliding with the stirring wall 67.
- the heat transfer rate can be improved.
- the bubbles can be promptly moved to the water outlet 23b despite the stirring of the washing water by the stirring wall 67. That is, since a linear vertical movement route is secured between the adjacent stirring walls 67 as described above, bubbles that are about to rise due to buoyancy or the like are not easily disturbed by the stirring wall 67, and are quickly Can rise to.
- FIG. 10 is a drawing showing still another configuration of the heat exchanger 10, and FIG. 10A shows the heat exchanger 10 with the second flow path forming member 22 removed and the base surface 30 a of the first flow path forming member 21. The structure when viewed from the side is shown, and (b) shows an example of the flow of washing water.
- the heat exchanger 10 (10D) has a substantially L-shaped rib 61 similar to that shown in the second embodiment, while the downstream space 25b Is provided with a stirring wall 67 similar to that shown in the third embodiment.
- the downstream space 25b is formed by the vertically upward water flow from the throttle channel 65a and the horizontal water flow from the throttle channel 65b.
- the water flow can also be stirred by the stirring wall 67 as described in the third embodiment. Therefore, the heat transfer coefficient can be further improved.
- the stirring wall 67 since the movement of bubbles is not easily disturbed by the stirring wall 67, the bubbles can be quickly moved upward and discharged to the outside from the water outlet 23b.
- FIG. 11 is a drawing showing still another configuration of the heat exchanger 10, and FIG. 11A shows the heat exchanger 10 with the second flow path forming member 22 removed and the base surface 30 a of the first flow path forming member 21.
- FIG. 2 shows a configuration when viewed from the side, (b) shows a BB section thereof, and (c) shows a CC section.
- the heat exchanger 10 (10E) which concerns on this Embodiment is provided with the structure same as what was shown in Embodiment 1, while Embodiment 1 is provided with a rib 71 having a slightly different configuration from that of the rib 31 according to the first embodiment. Accordingly, the configuration of the rib 71 will be described in detail below.
- the rib 71 is similar to the rib 31 of the first embodiment in that the X-direction one end 71a is near the upper side of the flow path space side opening of the water inlet 23a. It is in contact with the inner wall surface of the X direction one end side portion of the flange portion 32.
- the rib 71 extends from the one end portion 71a in the X direction on the base surface 30a along the X direction, and the other end portion 71b in the X direction abuts against the inner wall surface of the other end portion in the X direction of the flange portion 32. ing.
- the rib 71 is provided with a plurality of notches 72 at the tip thereof. These cutouts 72 are arranged at substantially equal intervals along the longitudinal direction of the rib 71 as shown in FIG. Moreover, as shown in FIG.11 (c), the end surface 74 of the front-end
- a slit-shaped throttle channel having an opening width dimension D1 is provided between the rib 71 and the first heat transfer surface 20a (indicated by a two-dot chain line) of the flat heater 20.
- 78, and a widened portion 78a having an opening width dimension D2 larger than the dimension D1 of the other portion is formed by the notch 72.
- illustration is abbreviate
- a throttle channel 78 having the same configuration is formed between the surface 20b.
- the opening width of the throttle channel 78 is not constant, and has a location of the dimension D1 and a location of the dimension D2 (> D1) in the widened portion 78a. It has become. Therefore, when the wash water flows from the upstream space 25a to the downstream space 25b via the throttle channel 78, the flow velocity differs between the water flow passing through the widened portion 78a and the water flow passing through other portions. As a result, the wash water is agitated by the plurality of water flows having different flow velocities in the downstream space 25b, and the heat transfer coefficient can be improved.
- the rib 71 exemplified here has a top portion 75 at the top of its tip portion, like the rib 31 shown in FIG. 7 (b). Not limited.
- a rib having a top at the bottom of the tip may be formed with a notch at the top.
- FIG. 12 is a drawing showing still another configuration of the heat exchanger 10.
- FIG. 12A shows the heat exchanger 10 with the second flow path forming member 22 removed, and the base surface 30 a of the first flow path forming member 21. A configuration when viewed from the side is shown, and (b) shows a cross-sectional view of the heat exchanger 10 taken along line BB.
- this heat exchanger 10 (10F) is equipped with the structure similar to the heat exchanger 10E which has the rib 71 demonstrated in Embodiment 5 (FIG. 11), Furthermore, The first flow path forming member 21 and the second flow path forming member 22 included in the heat exchanger 10F are extended in the horizontal direction (X direction) in the region corresponding to the downstream space 25b, and the vertical direction ( A plurality of buffer walls 81 arranged in parallel in the Z direction) are formed.
- the buffer wall 81 of the first flow path forming member 21 protrudes from the base surface 30 a by substantially the same dimension as the rib 71, and, like the rib 71, the other end side from the X direction one end side portion of the flange portion 32. It extends over the part. Further, as shown in FIG. 12B, the downstream space 25b is divided into a plurality of buffer spaces 82 (three buffer spaces 82a to 82c in the present embodiment) lined up and down by the buffer wall 81. The upper and lower adjacent buffer spaces 82 communicate with each other only through a slit-like throttle channel 83 formed between the buffer wall 81 and the first heat transfer surface 20a of the flat plate heater 20. A buffer wall 81 having the same configuration is also formed in the second flow path forming member 22.
- the height of the buffer wall 81 is set lower than the height of the rib 71.
- the wash water flowing into the lowermost buffer space 82a of the downstream space 25b through the throttle channel 78 formed by the rib 71 is turbulent and stirred. Further, since the buffer wall 81 is present at a position relatively close to the rib 71, a relatively high-speed water flow that has passed through the throttle channel 78 collides with the buffer wall 81, and the turbulent flow is generated in the buffer space 82a. Is promoted.
- the flow rate increases by passing through the narrow throttle channel 83.
- the speed of the water flow contacting the first heat transfer surface 20a of the flat heater 20 is increased, the heat transfer rate from the first heat transfer surface 20a to the washing water can be improved.
- the water flow having a high velocity collides with the next buffer wall 81 and the turbulent flow is promoted in the buffer space 82b, the heat transfer coefficient can be improved.
- the same phenomenon occurs in the buffer space 82c and the heat transfer coefficient is improved.
- the generated bubbles can be discharged upward.
- FIG. 13 is a drawing showing still another configuration of the heat exchanger 10.
- FIG. 13A shows the heat exchanger 10 with the second flow path forming member 22 removed and the base surface 30 a of the first flow path forming member 21. A configuration when viewed from the side is shown, and (b) shows a cross-sectional view of the heat exchanger 10 taken along line BB.
- the heat exchanger 10 (10G) has the same configuration as the heat exchanger 10F described in the sixth embodiment (FIG. 12), and further includes a buffer wall 81. A notch 88 is provided at an appropriate position.
- the heat exchanger 10G has three buffer walls 81 (81a to 81c) arranged vertically. These buffer walls 81a to 81c are provided with notches 88 so that the positions of the buffer walls 81a and 81b adjacent to each other in the vertical direction are different from each other when viewed in plan (Z direction view). In addition, the buffer walls 81b and 81c adjacent in the vertical direction are also provided with a notch 88 so that the positions thereof are different from each other.
- the lowermost buffer wall 81a is formed with one notch 88 near the center in the longitudinal direction (X direction).
- the buffer wall 81b thereabove is formed with cutouts 88 at two locations near one end in the longitudinal direction and near the other end.
- a notch 88 is formed in the buffer wall 81c thereabove in the vicinity of the central portion in the longitudinal direction, similar to the buffer wall 81a. Note that the number and positions of such notches 88 are examples, and as described above, the notches 88 are provided at locations different from the above as long as they do not overlap in the plan view in the adjacent buffer walls 81. Also good.
- the notch depth dimension and length dimension of the notch part 88 are not specifically limited.
- the washing water in each of the buffer spaces 82a to 82c flows upward through the narrow portion where the notch 88 is not formed in the throttle channel 78, and the widening due to the notch 88.
- the turbulent flow in the downstream space 25b is promoted, and the heat transfer rate from the flat heater 20 to the washing water is improved. Can be planned.
- FIG. 14 is a view showing a modification of the heat exchanger 10A described in the first embodiment, and the heat exchanger 10A with the second flow path forming member 22 and the flat heater 20 removed is formed with the first flow path. The structure when it sees from the base surface 30a side of the member 21 is shown.
- the ceiling surface (here, the inner upper surface of the first flow path forming member 21) 21a that defines the downstream space 25b is formed on an inclined surface that becomes lower as the distance from the vicinity of the water outlet 23b increases. .
- the inclined ceiling surface 21a is configured not only in the heat exchanger 10A according to the first embodiment, but also in other heat exchangers 10B to 10G described above, as well as the heat exchanger described below. It can also be applied to 10H to 10J.
- FIGS. 15A and 15B are diagrams showing the configuration of the heat exchanger 10 (10H), where FIG. 15A is a front view showing an external configuration, and FIG. 15B is a cross-sectional view taken along line BB.
- the heat exchanger 10H is configured to have a flat plate-like appearance having a small thickness dimension and a rectangular shape in front view, as shown in FIG. 15 (b).
- a flat plate heater 120 having a rectangular flat plate shape, a first flow path forming member 121 disposed opposite to one surface (first heat transfer surface) 120a, and the other surface (second heat transfer surface) 120b.
- the 2nd flow path formation member 122 arrange
- the flat heater 120 is made of ceramic
- the first flow path forming member 121 and the second flow path forming member 122 are made of reinforced ABS resin in which glass fiber is compounded with ABS resin.
- the vertical direction is the Z direction
- the direction perpendicular to this and parallel to the heat transfer surface of the flat plate heater 120 is the X direction
- the direction orthogonal to both of these two directions is taken as the Y direction.
- the first flow path forming member 121 is a rectangular flat base portion 130 that faces the first heat transfer surface 120 a and the first heat transfer surface 120 a that faces the base portion 130. And a plurality of wall portions (ribs) 131 protruding from the surface (base surface) 130a.
- the second flow path forming member 122 includes a rectangular flat base portion 140 that faces the second heat transfer surface 120b, and a surface (base surface) 140a that faces the second heat transfer surface 120b in the base portion 140. And a plurality of wall portions (ribs) 141 protruding from the wall.
- a wall-shaped flange portion 132 is provided around the periphery of the base portion 130 of the first flow path forming member 121, and the flange portion 132 is directed toward the second flow path forming member 122. It is extended by a predetermined dimension.
- An engaging groove 133 that circulates along the flange portion 132 is formed at the distal end portion of the flange portion 132.
- a wall-like flange portion 142 is also provided around the periphery of the base portion 140 of the second flow path forming member 122, and the flange portion 142 is directed away from the first flow path forming member 121. It is extended by a predetermined dimension. The front end portion of the flange portion 142 is folded back toward the first flow path forming member 121, and an engagement protrusion 143 that circulates along the flange portion 142 is formed at the end portion.
- the first flow path forming member 121 is externally fitted to the second flow path forming member 122 such that the base surface 130a faces the base surface 140a of the second flow path forming member 122. More specifically, the flange portion 132 of the first flow path forming member 121 is externally fitted to the flange portion 142 of the second flow path forming member 122, and further, the second flow is inserted into the engagement groove 133 of the first flow path forming member 121.
- the engagement protrusion 143 of the path forming member 122 is inserted (for example, the engagement protrusion 143 is fixed to the engagement groove 133 by ultrasonic welding). As a result, the first flow path forming member 121 and the second flow path forming member 122 are liquid-tightly joined, and a flow path space 125 is formed inside.
- a water inlet 123a is provided at the lower end of the casing 123 in the X direction, and a water outlet 123b is provided at the upper end of the casing 123. And as shown in FIG.15 (b), these water inlet 123a and the water outlet 123b are all connected to the said flow-path space 125. As shown in FIG. 15A, a water inlet 123a is provided at the lower end of the casing 123 in the X direction, and a water outlet 123b is provided at the upper end of the casing 123. And as shown in FIG.15 (b), these water inlet 123a and the water outlet 123b are all connected to the said flow-path space 125. As shown in FIG.
- FIG. 16 is a diagram when the heat exchanger 10H is disassembled, and FIG. 16A shows the heat exchanger 10H with the second flow path forming member 122 and the flat heater 120 removed, in the first flow path forming member 121.
- the base surface 130a of the base portion 130 of the first flow path forming member 121 has a plurality of (seven in this embodiment) walls extending along a substantially horizontal direction (X direction). Portions (ribs) 131 (131a to 131g) are arranged in parallel in the vertical direction (Z direction).
- odd-numbered wall portions (ribs) 131a, 131c, 131e, and 131g from the bottom are in contact with the inner wall surface of the flange portion 132 at one end portion in the longitudinal direction (one end portion in the X direction). Is separated from the inner wall surface of the flange portion 132 by a predetermined dimension.
- the even-numbered wall portions (ribs) 131b, 131d, and 131f from the bottom have one end portion in the longitudinal direction (one end portion in the X direction) separated from the inner wall surface of the flange portion 132, and the other end portion is a flange. It is in contact with the inner wall surface of the portion 132.
- meandering channels 135 defined by these wall portions (ribs) 131a to 131g are formed.
- the flow path 135a defined by the lower part of the flange part 132 and the lowermost wall part (rib) 131a allows cleaning water to flow from one side in the X direction where the water inlet 123a is located to the other side. Lead.
- the washing water that has reached the downstream end of the flow path 135a is folded back and passes through the flow path 135b defined by the wall portion (rib) 131a and the wall portion (rib) 131b above the X direction in the X direction. From the other side to the other side. Thereafter, similarly, the water is guided in the opposite direction while being sequentially folded along the flow paths 135c to 135h, and the washing water is guided to the water outlet 123b.
- These meandering channels 135a to 135h constitute a meandering channel 135 (see FIG. 19 described later).
- the wall portion (rib) 141 of the second flow path forming member 122 is symmetrical with the wall portion (rib) 131 of the first flow path forming member 121 described above. Since the configuration is the same except that the detailed description is omitted, the meandering flow path 145 from the water inlet 123a to the water outlet 123b is similarly configured.
- a rectangular flat plate heater 120 having a substantially constant thickness is provided so as to be sandwiched between the first flow path forming member 121 and the second flow path forming member 122 (see FIGS. 4 and 5). (Refer to the flat heater 20).
- FIG. 17 is a sectional view taken along line XVII-XVII of the heat exchanger 10H shown in FIG.
- the wall portion (rib) 131 has a longitudinal dimension (dimension in the X direction) of L1, and a height dimension H1 from the base surface 130a is substantially constant along the longitudinal direction. It has become.
- a notch 136 having an opening dimension (X-direction dimension) L2 and a depth dimension H2 is formed in the middle part in the longitudinal direction (the center part in the present embodiment).
- FIG. 18 is a drawing showing the configuration of the wall portion (rib) 131 and the notch 136
- FIG. 18A is a view of the portion XVIIIa of FIG. 17 to show the configuration when the notch 136 is viewed along the Z direction.
- An enlarged view, (b) is an enlarged view of a portion XVIIIb in FIG. 15 to show the configuration when the notch 136 is viewed along the X direction.
- the notch 136 has a shape in which the tip of the wall (rib) 131 is cut out in a rectangular shape, and is more than the other part of the wall (rib) 131.
- the deepest part 136 a is recessed and is formed substantially parallel to the upper end of the wall part (rib) 131.
- the front end surface of the wall portion (rib) 131 is not parallel to the surface of the flat heater 120 (the first heat transfer surface 120a), but at a predetermined angle A.
- the tip of the wall portion (rib) 131 is formed in a triangular shape so that the lower portion forms a top portion 137 having an acute cross section.
- the notch part 136 mentioned above is formed in this top part 137.
- FIG. By such a notch 136, a bypass path 138 is formed that communicates the lower flow path and the upper flow path defined by the wall portion (rib) 131.
- the separation dimension H3 is the following (2) with respect to the separation dimension H4 from the base surface 130a of the first flow path forming member 121 to the first heat transfer surface 120a.
- the wall portion (rib) 141 included in the second flow path forming member 122 is also arranged so as to satisfy the above formula (2) with the same cross-sectional shape as the wall portion (rib) 131, and A notch 146 that satisfies the equation (1) and has a depth dimension H2 is formed (see FIG. 18B).
- the notch 146 forms a bypass path 148 that communicates the upper and lower flow paths adjacent to each other with the wall (rib) 131 interposed therebetween.
- bypass channel 138 (or bypass channel) with respect to the cross-sectional area of the meandering channel 135 (or meandering channel 145). 148) can be secured more sufficiently, and bubbles can be guided to the water outlet 123b using the bypass channel 138 (or bypass channel 148) and discharged to the outside more easily and reliably. It becomes like this.
- the flow (flow rate) of water flowing from the upstream to the downstream of the one flow path 35a (or the flow path 145a positioned at the uppermost flow of the meandering flow path 145) positioned at the uppermost stream of the meandering flow path 135 is further facilitated. Ensuring sufficiently and eventually, the flow (flow rate) of water flowing from the upstream to the downstream of the meandering channel 135 (or the meandering channel 145) can be secured more easily and sufficiently, and the heat exchanger 10H The required heat exchange function of the original water can be more fully exhibited.
- the lower end portion of the flat heater 120 is positioned away from the lower inner wall surface of the flange portion 132 of the first flow path forming member 121. Therefore, the space below the lower end of the flat heater 120 is a space shared by the meandering channel 135 on the first heat transfer surface 120a side and the meandering channel 145 on the second heat transfer surface 120b side ( The upstream shared space) 125a, and the wash water that has entered the flow path space 125 from the water inlet 123a is distributed to the meandering flow paths 135 and 145 through the upstream shared space 125a. Similarly, as shown in FIG.
- the upper end of the flat heater 120 is positioned away from the upper inner wall surface of the flange portion 132 of the first flow path forming member 121, and the upper end of the flat heater 120 is The space above the section is a shared space (downstream shared space) 125b for the meandering channels 135 and 145. Therefore, the wash water flowing through the meandering channels 135 and 145 merges in the downstream shared space 125b and travels toward the water outlet 123b.
- FIG. 19 is a drawing showing the flow of washing water and bubbles in the heat exchanger 10H configured as described above, as seen from the base surface 130a side of the first flow path forming member 121, as in FIG. 16 (a). The structure of when is shown. As shown in FIG. 19, most of the low-temperature (for example, 5 ° C.) wash water that has entered from the water inlet 123a is moved upward in the order of the flow paths 135a to 135h while reversing the direction in one direction and the other in the X direction. It flows along the meandering flow path 135 (and the meandering flow path 145) (refer to the solid line arrow in FIG. 19).
- most of the low-temperature (for example, 5 ° C.) wash water that has entered from the water inlet 123a is moved upward in the order of the flow paths 135a to 135h while reversing the direction in one direction and the other in the X direction. It flows along the meandering flow path 135 (and the meander
- the temperature is raised to an appropriate temperature (for example, 40 ° C.) by heat transfer from the flat heater 120 and discharged from the water outlet 123b to the outside.
- an appropriate temperature for example, 40 ° C.
- action are demonstrated below.
- the wash water flowing in from the water inlet 123a of the casing 123 is heated while flowing through the flow path 135 defined by the heat transfer surface on the surface of the flat heater 120, and the temperature gradually increases as it approaches the water outlet 123b. To do.
- the surface temperature of the flat heater 120 near the water inlet 123a tends to become high due to the relatively high heat generation density, but because a lot of heat is taken away by the low temperature washing water that has not yet been heated, The temperature is not high enough to cause local boiling.
- the washing water is hotter in the portion near the water outlet 123b than in the portion near the water inlet 123a, the amount of heat taken away by the washing water on the surface of the flat heater 120 in the portion is reduced. Since the heat generation density in the portion near the water outlet 123b is smaller than the heat generation density in the portion near the water inlet 123a, the portion does not reach such a high temperature that a local boiling phenomenon occurs.
- the flat heater 120 is configured such that the heat generation density in the portion near the water outlet 123b is smaller than the heat generation density in the portion near the water inlet 123a, the temperature of the water outlet 123b in which the temperature of the washing water increases. Even at the boundary surface between the flat heater 120 and water in a portion close to, a high temperature at which a local boiling phenomenon occurs is suppressed. As a result, scale generation and adhesion can be prevented, and a long-life heat exchanger can be realized.
- the heat of the flat heater 120 is transferred to the cleaning water flowing in contact with the heat transfer surfaces on both the front and back surfaces, and heat exchange with high heat efficiency with almost no heat loss.
- the size can be reduced.
- the flow path length can be increased and the flow velocity can be increased by the meandering flow paths 135 and 145, the boundary layer that is substantially transferred from the surface of the flat heater 120 in the washing water flowing through the meandering flow paths 135 and 145.
- the thickness becomes thinner. Therefore, the heat transfer efficiency can be improved and the temperature rise of the heater surface can be suppressed, so that the local boiling phenomenon can be suppressed and the effect of preventing the generation and adhesion of scale can be further enhanced.
- the heat generation density in the portion near the water outlet 123b is formed smaller than the heat generation density in the portion near the water inlet 123a.
- the effect brought about to the heat exchanger 10H which concerns on this Embodiment by such a structure is the same as that of having demonstrated in Embodiment 1 mentioned above.
- the meandering channel 135 (or the meandering channel 145) is defined by a plurality of walls 131 that extend in a substantially horizontal direction and are arranged in parallel in the vertical direction.
- the meandering channel 135 (or the meandering channel 145) from the water inlet 123a to the water outlet 123b, the channel 135a that guides the cleaning water in one direction in the substantially horizontal direction and the channel 135b that guides the cleaning water in the other direction alternate.
- a vertical bypass path 138 (or a bypass flow path 148) communicating with the upper and lower adjacent flow paths 135 is provided in the middle portion of the wall 131 in the longitudinal direction. ) Is formed.
- the heat transfer rate can be improved by flowing the cleaning water at a high speed, and the vertical bypass path 138 (or bypass path) formed in the middle of the meandering channel 135 (or the meandering channel 145). 148), the bubbles can be promptly guided to the water outlet 123b.
- the meandering channel 135 is provided in the heat exchanger 10H and the channel cross-sectional area is small, the flow rate of the cleaning water can be increased and uniformized. Further, as described above, the flat heater 120 has a heat generation density in a portion near the water outlet 123b that is lower than a heat generation density in a portion near the water inlet 123a, and becomes a high temperature that causes a local boiling phenomenon. Therefore, the generation of bubbles is also suppressed. On the other hand, even if bubbles are generated, vertical bypass passages 138 and 148 for short-cutting the meandering passages 135 and 145 having a long passage for guiding the washing water from the water inlet 123a to the water outlet 123b are provided. Since it is provided, the generated bubbles can be quickly moved to the water outlet 123b through the bypass path 138 (or bypass path 148) through the channel length shorter than the total length of the meandering channel 135.
- the flow path resistance on the one heat transfer surface 120a (or 120b) side of the flat heater 120 becomes extremely larger than the other due to bubbles, or one heat transfer surface 120a of the flat heater 120. Only the temperature of (or 120b) can be prevented from greatly increasing, and the local boiling phenomenon that causes generation and adhesion of scale can be further suppressed. Further, since the bubbles generated on the surface of the flat heater 120 are quickly discharged to the water outlet 123b by the bypass passage 138 (or the bypass passage 148), it is possible to suppress the bubble from growing large, and the large bubbles are discharged from the outlet. Inhibiting the operation of the thermistor near 123b can be prevented.
- the meandering channels 135 and 145 and the bypass channels 138 and 148 are symmetrical on one heat transfer surface 120a side and the other heat transfer surface 120b side of the flat heater 120. It is the structure formed automatically. Thereby, the balance of the heat transfer amount between the heat transfer surfaces on the front and back sides of the flat heater 120 can be suitably ensured, and deformation of the flat heater 120 due to thermal stress can be prevented.
- the heat exchanger 10H of the present embodiment has a configuration in which the bypass passages 138 formed in the plurality of wall portions 131 arranged in the vertical direction are provided so that the positions when viewed in plan are substantially coincident with each other. Yes.
- the bypass passages 148 formed on the plurality of wall portions 141 arranged in the vertical direction are also provided so that their positions substantially coincide with each other when viewed in plan.
- the bubbles can rise straight upward through the bypass paths 138 and 148 and can quickly reach the water outlet.
- the gas component dissolved in the cleaning water may be vaporized again to generate bubbles. Describing such a flow of bubbles (see the white arrow in FIG. 19), for example, bubbles generated in the flow path 135a of the meandering flow path 135 flow through the flow path 135a together with the cleaning water. However, since the buoyancy force that moves the washing water upward is acting on the bubbles, the bypass passage 138 including the notch 136 formed in the wall (rib) 131a before reaching the downstream end of the flow path 135a. And move to the channel 135b adjacent on the upper side as a shortcut.
- bubbles generated inside can be quickly guided to the water outlet 123b and discharged to the outside.
- FIG. 20A and 20B are enlarged views of the notch when viewed along the Z direction in order to show another configuration of the notch.
- FIG. 20A is a diagram in which the deepest part of the notch is tapered
- FIG. 20B is a notch.
- the deepest part of the part has an arc shape
- (c) shows that the deepest part has an inclined surface.
- the notch 150 shown in FIG. 20A has a notch width dimension (X dimension) that decreases as the notch depth dimension (Y dimension) from the tip of the wall (rib) 131 increases.
- the deepest portion 151 is tapered.
- the notch 150 has a deepest portion 151 that is one step deeper from the tip of the wall (rib) 131 when viewed in plan, and this deepest portion 151 is a depth dimension of a substantially central portion in the X direction. It has an inclined contour so that is the largest.
- 154 is formed in an arc shape.
- the deepest surface 157 is inclined so that the notch depth increases from the upstream end 157a to the downstream end 157b in the washing water flow direction. Is made.
- FIG. 21 is a diagram showing another configuration of the heat exchanger, and shows the configuration when viewed from the base surface 130a side of the first flow path forming member 121.
- the opening dimension L2 of the notch 136 is made different according to each wall (rib) 131a to 131g. More specifically, the cutout portion 136 of the wall portion (rib) 131a located at the lowest position is formed so that the opening dimension L2 is the smallest. Then, the opening dimension L2 of each notch 136 is increased in the order of the wall parts (ribs) 131b to 131f, and the notch part 136 of the uppermost wall part (rib) 131g has the largest opening dimension L2. Is formed. Since other configurations are the same as those of the heat exchanger 10H described in the ninth embodiment, description thereof is omitted here.
- the heat exchanger 10I having such a configuration, it is possible to increase the flow rate of the cleaning water along the meandering flow paths 135 and 145, and it is possible to improve the heat conductivity and the bubble conveyance efficiency.
- not only bubbles but also cleaning water may flow through the bypass passages 138 and 148 including the notches 136 as shortcuts.
- the notch portion 136 formed in the wall portion (rib) 131 can be reduced by reducing the opening dimension L2.
- the wall (rib) 131 that defines the relatively upper flow path in which bubbles are likely to be generated is generated by forming the notch 136 so as to have a relatively large opening dimension L2. The bubbles can be moved to the upper flow path with a more reliable shortcut.
- the opening dimensions L2 of the notches 136 provided in all the walls (ribs) 131 are different from each other.
- the present invention is not limited to this.
- the opening dimension L2 of the notches 136 of the two walls (ribs) 131a and 131b positioned below is set to the same minimum value, and the notches 136 of the two walls (ribs) 131f and 131g positioned above are formed.
- the same maximum value may be used, and the notches 136 of the three wall portions (ribs) 131c to 131e located in the middle may have the same predetermined value (a predetermined value between the minimum value and the maximum value). .
- the opening dimension L2 of the notch 136 is larger in the uppermost wall (rib) 131g than in the lowermost wall (rib) 131a, and between these wall (rib) 131 and 131g.
- the wall portion (rib) 131b to 131f that are positioned the wall portion (rib) 131 that is positioned above the relatively lower wall portion (rib) 131 has a smaller opening dimension L2 of the notch 136. It should be set so as not to become.
- FIG. 22 is a drawing showing still another configuration of the heat exchanger, and shows the configuration when viewed from the base surface 130 a side of the first flow path forming member 121.
- the notch 136 is formed only for the upper part of the wall part (rib) 131 (here, the upper two wall parts (ribs) 131f and 131g). In other words, notches 136 are not formed in the other walls (ribs) 131 (131a to 131e).
- the heat exchanger 10J having such a configuration, in the lower flow path where the probability of bubble generation is low, the washing water is prevented from moving through the notch 136 and the flow rate is improved. Bubbles generated in the upper flow path that is heated can be moved upward through the notch 136 and quickly discharged from the water outlet 123b.
- the wall portions (ribs) 131 to be formed with the notches 136 are not limited to the two cases as shown in FIG. 22, but depend on the degree of generation of bubbles in each flow path, the flow rate of cleaning water, and the like. May be set as appropriate. Therefore, only one of the uppermost wall portions (ribs) 131g may be used, or the upper three wall portions (ribs) 131e to 131g may be used, or a larger number may be targeted.
- the present invention can be applied to a long-life flat plate heat exchanger that can suppress the generation and adhesion of scale while improving the heat transfer coefficient, and can quickly guide the generated bubbles to the outlet. it can.
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Abstract
Description
図1は、本発明の実施の形態に係る熱交換器を備える衛生洗浄装置を示す外観斜視図である。図1に示すように、衛生洗浄装置1は便器2の上面に配設されており、本体部3、便座部4、便蓋部5、および操作部6などを備えている。このうち本体部3は、便座部4の後側(着座した使用者から見て背後側)に配設されており、横長で中空の筐体3a内に、図示しない洗浄ユニット、乾燥ユニット、およびこれらの動作を制御する制御ユニットの他、本実施の形態に係る熱交換器10(破線で図示)などが収納されている。この熱交換器10には、便器2の設置建物に付随の水道設備から水道水(流体,液体,洗浄水)が導入され、内部で適温にまで暖められる。そして、使用者が操作部6を操作して所定の入力を行うと、洗浄ユニットが駆動して、該洗浄ユニットが有するノズルからシャワー状に人体局部に対して洗浄水が噴射されるようになっている。
[熱交換器]
図2,図3は、熱交換器10(10A)の構成を示す図面であり、図2は外観構成を示す正面図、図3は図2のB-B線での断面図を夫々示している。図2,図3に示すように、熱交換器10Aは厚み寸法が小さく正面視で長方形状を成す平板状の外観形状に構成されており、図3に示すように、矩形平板状を成す平板状ヒータ20と、その一方の面(第一伝熱面)20aに対向配置された第一流路形成部材21と、他方の面(第二伝熱面)20bに対向配置された第二流路形成部材22と、これらを収容して入水口23aおよび出水口23bを有するケーシング23とを備えている。このうち平板状ヒータ20はセラミック製であり、第一流路形成部材21および第二流路形成部材22は、ABS樹脂にガラス繊維をコンパウンドした強化ABS樹脂製としている。
以上のように本実施の形態は、平板状ヒータ20の出水口23bに近い部分の発熱密度が入水口23aに近い部分の発熱密度より小さくなるように形成されている。また、流路スペース25は、入水口23aの開口部を含む上流側スペース25aと、出水口23bの開口部を含む下流側スペース25bとを有し、上流側スペース25aと下流側スペース25bとの間には、他の部分よりも通流断面積の小さい絞り流路37,47が設けられている。これらにより、ケーシング23の入水口23aから流入した洗浄水は、平板状ヒータ20の伝熱面によって画定される流路スペース25を流れながら加熱され、出水口23bに近づくにしたがって温度が次第に上昇する。
図8は、熱交換器10の他の構成を示す図面であり、(a)は第二流路形成部材22を取り外した状態の熱交換器10を第一流路形成部材21のベース面30a側から見たときの構成を示し、(b)は洗浄水の流れの一例を示している。図8(a)に示すように、この熱交換器10(10B)では、入水口23a近傍から水平方向へ延びるリブ61を有し、該リブ61は途中で屈曲して垂直方向上方へ向かって延設された構成となっている。
図9は、熱交換器10のさらに他の構成を示す図面であり、(a)は第二流路形成部材22を取り外した状態の熱交換器10を第一流路形成部材21のベース面30a側から見たときの構成を示し、(b)は洗浄水の流れの一例を示している。図9(a)に示すように、この熱交換器10(10C)は実施の形態1に示したものと同様の真直ぐ且つ水平なリブ31を有している一方、下流側スペース25b内に、波形形状を成す複数の撹拌壁67が設けられている。
図10は、熱交換器10のさらに他の構成を示す図面であり、(a)は第二流路形成部材22を取り外した状態の熱交換器10を第一流路形成部材21のベース面30a側から見たときの構成を示し、(b)は洗浄水の流れの一例を示している。図10(a)に示すように、この熱交換器10(10D)は実施の形態2に示したものと同様の略L字状のリブ61を有している一方、下流側スペース25b内には、実施の形態3に示したものと同様の撹拌壁67が設けられている。
図11は、熱交換器10のさらに他の構成を示す図面であり、(a)は第二流路形成部材22を取り外した状態の熱交換器10を第一流路形成部材21のベース面30a側から見たときの構成を示し、(b)はそのB-B断面を示し、(c)はC-C断面を示している。図11(a)に示すように、本実施の形態に係る熱交換器10(10E)は、実施の形態1にて示したものと大部分において同一の構成を備えている一方、実施の形態1に係るリブ31とは若干異なる構成のリブ71を備えている。従って、以下ではこのリブ71の構成に関して詳しく説明する。
図12は、熱交換器10のさらに他の構成を示す図面であり、(a)は第二流路形成部材22を取り外した状態の熱交換器10を第一流路形成部材21のベース面30a側から見たときの構成を示し、(b)は当該熱交換器10のB-B線での断面図を示している。
図13は、熱交換器10のさらに他の構成を示す図面であり、(a)は第二流路形成部材22を取り外した状態の熱交換器10を第一流路形成部材21のベース面30a側から見たときの構成を示し、(b)は当該熱交換器10のB-B線での断面図を示している。図13(a)に示すように、この熱交換器10(10G)は、実施の形態6(図12)にて説明した熱交換器10Fと同様の構成を備えており、さらに、バッファ壁81の適所に切欠部88が設けられている。
次に、流路スペースに、入水口から水平方向の一方向へ洗浄水を導く流路と他方向へ導く流路とが交互に下方から上方へ設けられて出水口へ至る蛇行流路と、該蛇行流路において上下に隣接する流路間を連通する上下方向のバイパス路とを形成した熱交換器について、実施の形態8~11にて説明する。なお、これらの実施の形態に示す各熱交換器10は、何れも図1に示した衛生洗浄装置1の熱交換器10として適用可能なものである。また、既に説明したように、以下に説明する熱交換器10が備える平板状ヒータ120は、図4,図5を用いて説明した平板状ヒータ20(特に、抵抗体のパターン20pに関する構成)と同様の構成を備えている。
[熱交換器]
図15は、熱交換器10(10H)の構成を示す図面であり(a)は外観構成を示す正面図、(b)はB-B線での断面図を夫々示している。図15(a),(b)に示すように、熱交換器10Hは厚み寸法が小さく正面視で長方形状を成す平板状の外観形状に構成されており、図15(b)に示すように、矩形平板状を成す平板状ヒータ120と、その一方の面(第一伝熱面)120aに対向配置された第一流路形成部材121と、他方の面(第二伝熱面)120bに対向配置された第二流路形成部材122と、これらを収容して1入水口23a及び出水口123bを有するケーシング123とを備えている。このうち平板状ヒータ120はセラミック製であり、第一流路形成部材121及び第二流路形成部材122は、ABS樹脂にガラス繊維をコンパウンドした強化ABS樹脂製としている。
1/2≧(L2/L1)≧1/5 ・・・(1)
を満たすように設定されている。例えば、L2=20mmとすることができる。
1/4≧(H3/H4)≧1/10 ・・・(2)
を満たすように設定されている。例えば、H3=0.2mm、H4=1.9mmとすることができる。
図20は、切欠部の他の構成を示すべく切欠部をZ方向に沿って見たときの拡大図であり、(a)は切欠部の最深部がテーパ状のもの、(b)は切欠部の最深部が円弧状のもの、(c)は最深部が傾斜面のものを夫々示している。
図21は、熱交換器の他の構成を示す図面であり、第一流路形成部材121のベース面130a側から見たときの構成を示している。図21に示す熱交換器10(10I)では、切欠部136の開口寸法L2を各壁部(リブ)131a~131gに応じて異ならせている。より詳しく説明すると、最も下方に位置する壁部(リブ)131aの切欠部136については、開口寸法L2が最も小さくなるように形成する。そして、壁部(リブ)131b~131fの順に各切欠部136の開口寸法L2を大きくしていき、最も上方に位置する壁部(リブ)131gの切欠部136は開口寸法L2が最も大きくなるように形成している。その他の構成については、実施の形態9において説明した熱交換器10Hと同様であるため、ここではその説明は省略する。
図22は、熱交換器の更に他の構成を示す図面であり、第一流路形成部材121のベース面130a側から見たときの構成を示している。図22に示す熱交換器10(10J)では、上側の一部の壁部(リブ)131(ここでは、上側の2つの壁部(リブ)131f,131g)についてのみ、切欠部136を形成することとし、その他の壁部(リブ)131(131a~131e)には切欠部136を形成していない。
10,10A~10J 熱交換器
20,120 平板状ヒータ
20a,120a 第一伝熱面
20b,120b 第二伝熱面
20h ヒータ線間隔
20k セラミック基体
20p パターン
20s ヒータ線幅
21,121 第一流路形成部材
22,122 第二流路形成部材
23,123 ケーシング
23a,123a 入水口
23b,123b 出水口
25 流路スペース
25a 上流側スペース
25b 下流側スペース
30,40 ベース部
31,41,61,71 リブ
31a,31b,61a,61b,61c,71a,71b 端部
37,38,47,48,65,78,83 絞り流路
65a 水平絞り流路
65b 垂直絞り流路
67 撹拌壁
72,88,136,150,153,156 切欠部
78a 拡幅部
81,81a,81b,81c バッファ壁
131,131a~131g,141 壁部(リブ)
135,135a~135h,145 蛇行流路
138,148 バイパス路
Claims (23)
- 入水口及び出水口を有するケーシングと、
該ケーシング内に配設されて表面が伝熱面を成すヒータと、
前記ケーシング内に形成され、前記入水口から流入した流体が前記ヒータの伝熱面との間で熱交換されつつ前記出水口に至るように案内する流路スペースとを備え、
前記ヒータは、前記出水口に近い部分の発熱密度が前記入水口に近い部分の発熱密度より小さく形成されていることを特徴とする熱交換器。 - 前記ヒータは、鉛直方向に対して略平行に配置された平板状ヒータであって、表裏2つの主面が前記伝熱面を成しており、
前記流路スペースは、前記平板状ヒータの表裏の前記伝熱面の夫々に沿って、下部の前記入水口から上部の前記出水口まで形成されている、請求項1に記載の熱交換器。 - 前記ヒータは、セラミック基体と、該セラミック基体上に抵抗体をパターン印刷して形成された発熱抵抗体と、電極とから成るセラミックヒータであり、前記印刷パターンの線幅は、前記入水口に近い部分より前記出水口に近い部分の方が太く形成されている、請求項1又は2に記載の熱交換器。
- 前記ヒータは、セラミック基体と、該セラミック基体上に抵抗体をパターン印刷して形成された発熱抵抗体と、電極とから成るセラミックヒータであり、前記印刷パターンの線間の隙間は、前記入水口に近い部分より前記出水口に近い部分の方が狭く形成されている、請求項1又は2に記載の熱交換器。
- 前記流路スペースは、前記入水口の開口部を含む上流側スペースと、前記出水口の開口部を含む下流側スペースとを有し、前記上流側スペースと前記下流側スペースとの間には、他の部分よりも通流断面積の小さい絞り流路が設けられている、請求項2乃至4の何れかに記載の熱交換器。
- 前記流路スペースは、前記平板状ヒータの一方の伝熱面側と他方の伝熱面側とで対称的に形成されている、請求項5に記載の熱交換器。
- 前記上流側スペースよりも前記下流側スペースの方が大きい容量を有している、請求項5又は6に記載の熱交換器。
- 前記絞り流路は、前記下流側スペースへ向けて上向きに流体を流入させるべく、前記入水口近傍から略水平方向に向かって延設された水平絞り流路を有している、請求項5~7の何れかに記載の熱交換器。
- 前記絞り流路は、前記下流側スペースへ向けてさらに水平向きに流体を流入させるべく、前記水平絞り流路において前記入水口から離隔する方の端部から、略垂直上方へ向かって延設された垂直絞り流路を有している、請求項8に記載の熱交換器。
- 前記絞り流路はスリット状を成し、該絞り流路は、他の部分よりも開口幅寸法の大きい拡幅部を有する、請求項5~9の何れかに記載の熱交換器。
- 前記下流側スペースには、流体を撹拌させるための撹拌壁が前記平板状ヒータに沿って略上下方向に延設されており、前記撹拌壁は、水平方向に波打った形状を有している、請求項5~10の何れかに記載の熱交換器。
- 前記下流側スペースには、前記平板状ヒータに沿って略水平方向へ延設されたバッファ壁が設けられている、請求項5~11の何れかに記載の熱交換器。
- 前記バッファ壁は上下方向に複数並設されており、該バッファ壁には、平面視したときに上下に隣接するバッファ壁において互いに位置が異なるように切欠部が形成されている、請求項12に記載の熱交換器。
- 前記平板状ヒータを挟んで配設される一対の流路形成部材を備え、
前記流路形成部材は、前記平板状ヒータに対面配置される平板状のベース部と、該ベース部における前記平板状ヒータとの対向面に突設されたリブとを有し、
前記リブとこれに対向する前記平板状ヒータとによって、両者間にスリット状の前記絞り流路が構成されている、請求項5~13の何れかに記載の熱交換器。 - 前記ヒータは、鉛直方向に対して略平行に配置された平板状ヒータであって、表裏2つの主面が前記伝熱面を成しており、
前記流路スペースは、前記平板状ヒータの表裏の前記伝熱面の夫々に沿って、下部の前記入水口から上部の前記出水口まで延設された蛇行流路に形成されている、請求項1に記載の熱交換器。 - 前記蛇行流路は、略水平方向へ延びて鉛直方向に並設された複数の壁部により画定され、前記入水口から前記出水口まで、流体を略水平方向の一方向へ導く流路と他方向へ導く流路とが交互に下方から上方へ設けられた構成となっており、
前記壁部の長手方向の途中部分には、上下に隣接する前記流路を連通する上下方向のバイパス路が形成されている、請求項15に記載の熱交換器。 - 前記蛇行流路及び前記バイパス路は、前記平板状ヒータの一方の伝熱面側と他方の伝熱面側とで対称的に形成されている、請求項16に記載の熱交換器。
- 複数の前記壁部に形成された前記バイパス路は、平面視したときの位置が略一致するようにして設けられている、請求項16又は17に記載の熱交換器。
- 前記平板状ヒータを挟んで配設される一対の流路形成部材を備え、
該流路形成部材は、前記平板状ヒータに対面配置される平板状のベース部と、該ベース部における前記平板状ヒータとの対向面に突設されて前記壁部を成す複数のリブと、を有し、
前記リブの長手方向の途中部分には、他の部分よりも該リブの先端が窪んで前記バイパス路を成す切欠部が形成されている、請求項16~18の何れかに記載の熱交換器。 - 前記リブの切欠部は、切り欠き深さが大きくなるに従って切り欠き幅が小さくなるように平面視でテーパ状を成している、請求項19に記載の熱交換器。
- 前記リブの切欠部は、切り欠き幅の中央部分の切り欠き深さが大きくなるように平面視で円弧状を成している、請求項19に記載の熱交換器。
- 相対的に下方に設けられた前記リブよりも上方に設けられた前記リブの方が、切欠部の切り欠き幅が大きく形成されている、請求項19~21の何れかに記載の熱交換器。
- 相対的に下方に設けられた前記リブには前記切欠部が形成されておらず、相対的に上方に設けられた前記リブに対して前記切欠部が形成されている、請求項19~21の何れかに記載の熱交換器。
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JP2012225621A (ja) * | 2011-04-22 | 2012-11-15 | Panasonic Corp | 熱交換器 |
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CN104011479A (zh) * | 2012-12-17 | 2014-08-27 | 松下电器产业株式会社 | 热交换器及具备该热交换器的卫生清洗装置 |
CN104011479B (zh) * | 2012-12-17 | 2015-05-13 | 松下电器产业株式会社 | 热交换器及具备该热交换器的卫生清洗装置 |
WO2014097346A1 (ja) * | 2012-12-17 | 2014-06-26 | パナソニック株式会社 | 熱交換器およびそれを備える衛生洗浄装置 |
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TW201114398A (en) | 2011-05-01 |
KR20120060226A (ko) | 2012-06-11 |
EP2476969A1 (en) | 2012-07-18 |
CN102483260A (zh) | 2012-05-30 |
JP2012002491A (ja) | 2012-01-05 |
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