U.S. patent application number 13/390882 was filed with the patent office on 2012-06-14 for heat exchanger.
Invention is credited to Ryoichi Koga.
Application Number | 20120148220 13/390882 |
Document ID | / |
Family ID | 46199479 |
Filed Date | 2012-06-14 |
United States Patent
Application |
20120148220 |
Kind Code |
A1 |
Koga; Ryoichi |
June 14, 2012 |
HEAT EXCHANGER
Abstract
Provided is a heat exchanger capable of suppressing formation
and adhesion of scale while achieving a higher heat transfer rate,
and having a longer life. A heat exchanger 10 includes throttle
passages 37 and 47 having smaller flow passage cross-sectional
areas than another portion between an upstream space 25a and a
downstream space 25b, and a plate heater 20 configured in such a
manner that a heat generation density is lower in a portion closer
to a water outlet 25b than in a portion closer to a water inlet
25a. This makes it possible to suppress a temperature from rising
to a high temperature at which local boiling will take place, even
in a boundary layer between a portion of the plate heater 20 which
is closer to the water outlet 25b, where the temperature of the
washing water tends to be high, and washing water contacting the
portion of the plate heater 20 which is closer to the water outlet
25b, while improving the heat transfer rate. As a result,
generation of air bubbles is suppressed, and the generated air
bubbles are guided quickly to the water outlet 25b. Thus, a heat
exchanger which can prevent formation of scale and adhesion of the
scale onto the plate heater 20 and has a longer like is
provided.
Inventors: |
Koga; Ryoichi; (Shiga,
JP) |
Family ID: |
46199479 |
Appl. No.: |
13/390882 |
Filed: |
September 6, 2010 |
PCT Filed: |
September 6, 2010 |
PCT NO: |
PCT/JP2010/005459 |
371 Date: |
February 16, 2012 |
Current U.S.
Class: |
392/485 |
Current CPC
Class: |
F24H 9/0015 20130101;
F24H 1/102 20130101; E03D 9/08 20130101; H05B 2203/037 20130101;
H05B 3/283 20130101; H05B 2203/013 20130101; H05B 2203/003
20130101; F24D 19/0092 20130101 |
Class at
Publication: |
392/485 |
International
Class: |
F24H 1/10 20060101
F24H001/10 |
Foreign Application Data
Date |
Code |
Application Number |
Sep 7, 2009 |
JP |
2009-206224 |
Sep 7, 2009 |
JP |
2009-206233 |
Mar 23, 2010 |
JP |
2010-066171 |
May 19, 2010 |
JP |
2010-114910 |
Claims
1. A heat exchanger comprising: a casing having a water inlet and a
water outlet; a heater disposed inside the casing and having
surfaces serving as heat transfer surfaces; and a passage space
provided inside the casing, to guide a fluid which has flowed into
the heat exchanger through the water inlet to the water outlet, the
fluid being guided to the water outlet while exchanging heat with
the heat transfer surfaces of the heater; characterized in that the
heater is configured in such a manner that a heat generation
density in a portion closer to the water outlet is lower than a
heat generation density in a portion closer to the water inlet.
2. The heat exchanger according to claim 1, wherein the heater is a
plate heater placed to be oriented in a direction substantially
parallel to a vertical direction, and has an obverse main surface
and a reverse main surface which are the heat transfer surfaces;
and the passage space extends from the water inlet at a lower
portion to the water outlet at an upper portion along the obverse
and reverse heat transfer surfaces of the plate heater.
3. The heat exchanger according to claim 1, wherein the heater is a
ceramic heater including a ceramic base body, a heat generation
resistive element formed by printing a pattern of a resistive
element on the ceramic base body, and an electrode, and the printed
pattern has a line width greater in a portion of the heater which
is closer to the water outlet than in a portion of the heater which
is closer to the water inlet.
4. The heat exchanger according to claim 1, wherein the heater is a
ceramic heater including a ceramic base body, a heat generation
resistive element formed by printing a pattern of a resistive
element on the ceramic base body, and an electrode, and the printed
pattern has a line interval greater in a portion of the heater
which is closer to the water outlet than in a portion of the heater
which is closer to the water inlet.
5. The heat exchanger according to claim 2, wherein the passage
space includes an upstream space including an opening of the water
inlet and a downstream space including an opening of the water
outlet, and a throttle passage having a smaller flow passage
cross-sectional area than another space is provided between the
upstream space and the downstream space.
6. The heat exchanger according to claim 5, wherein the passage
space at one heat transfer surface side of the plate heater and the
passage space at the other heat transfer surface side of the plate
heater are symmetric.
7. The heat exchanger according to claim 5, wherein the downstream
space has a greater volume than the upstream space.
8. The heat exchanger according to claim 5, wherein the throttle
passage has a horizontal throttle passage extending substantially
horizontally from a portion of the heat exchanger which is closer
to the water inlet, to flow the fluid in an upward direction toward
the downstream space.
9. The heat exchanger according to claim 8, wherein the throttle
passage has a vertical throttle passage extending substantially
vertically upward, from one end portion of the horizontal throttle
passage which is farther from the water inlet than the other end
portion of the horizontal throttle passage, to flow the fluid
horizontally toward the downstream space.
10. The heat exchanger according to claim 5, wherein the throttle
passage has a slit shape; and the throttle passage has an
increased-width portion having a greater opening width than another
portion.
11. The heat exchanger according to claim 5, wherein an agitating
wall for agitating the fluid is provided in the downstream space to
extend in a substantially upward and downward direction along the
plate heater; and the agitating wall is corrugated to have a
horizontal amplitude.
12. The heat exchanger according to claim 5, wherein a buffer wall
extending substantially horizontally along the plate heater is
provided in the downstream space.
13. The heat exchanger according to claim 12, wherein the buffer
wall has a plurality of buffer walls arranged in the upward and
downward direction; and the buffer walls are provided with
remaining portions formed by cutting portions of the buffer walls
such that positions of the remaining portions are different between
adjacent upper and lower buffer walls when viewed from above.
14. The heat exchanger according to claim 5, comprising: a pair of
passage forming members disposed to sandwich the plate heater;
wherein each of the passage forming members includes a base portion
of a plate shape disposed to face the plate heater, and a rib
protruding from a surface of the base portion which faces the plate
heater; and the slit-shape throttle passage is defined by the rib
and the plate heater which faces the rib, and is provided between
the rib and the plate heater which faces the rib.
15. The heat exchanger according to claim 1, wherein the heater is
a plate heater placed to be oriented in a direction substantially
parallel to a vertical direction, and has an obverse main surface
and a reverse main surface which are the heat transfer surfaces;
and the passage space is formed in a sinuous passage extending from
the water inlet at a lower portion to the water outlet at an upper
portion along the obverse and reverse heat transfer surfaces of the
plate heater.
16. The heat exchanger according to claim 15, wherein the sinuous
passage is defined by a plurality of wall portions arranged
vertically to extend substantially horizontally; the sinuous
passage has, in a range from the water inlet to the water outlet, a
passage for guiding the fluid in one direction in a substantially
horizontal direction, and a passage for guiding the fluid in an
opposite direction in the substantially horizontal direction such
that the passages are arranged alternately from a lower side to an
upper side; and a bypass passage is provided in an upward and
downward direction on a portion of each of the wall portions in a
longitudinal direction thereof to provide communication between
adjacent upper and lower passages.
17. The heat exchanger according to claim 16, wherein the sinuous
passage at one heat transfer surface side of the plate heater and
the sinuous passage at the other heat transfer surface side of the
plate heater are symmetric; and the bypass passage at one heat
transfer surface side of the plate heater and the bypass passage at
the other heat transfer surface side of the plate heater are
symmetric.
18. The heat exchanger according to claim 16, wherein bypass
passages formed on the plurality of wall portions substantially
conform in position to each other when viewed from above.
19. The heat exchanger according to claim 16, comprising: a pair of
passage forming members disposed to sandwich the plate heater;
wherein each of the passage forming members includes a base portion
of a plate shape disposed to face the plate heater, and a plurality
of ribs protruding from a surface of the base portion which faces
the plate heater to form the wall portions; and a remaining portion
formed by cutting a portion of each of the plurality of ribs is
provided on a portion of each of the plurality of ribs in a
longitudinal direction thereof such that a tip end of the rib is
dented with respect to another portion to form the bypass
passage.
20. The heat exchanger according to claim 19, wherein the remaining
portion of the rib has a tapered shape when viewed from above such
that a cut portion width of the remaining portion decreases as a
cut portion depth of the remaining portion increases.
21. The heat exchanger according to claim 19, wherein the remaining
portion of the rib has a circular-arc shape when viewed from above
such that a cut portion depth of a center portion of a cut portion
width is greater.
22. The heat exchanger according to claim 19, wherein the remaining
portion of the rib provided at a relatively upper side has a
greater cut portion width than the remaining portion of the rib
provided at a relatively lower side.
23. The heat exchanger according to claim 19, wherein the remaining
portion is not provided on the rib provided at a relatively lower
side; and the remaining portion is provided on the rib provided at
a relatively upper side.
Description
TECHNICAL FIELD
[0001] The present invention relates to a heat exchanger of an
instantaneous heating type, for use with a sanitary washing device
capable of washing a private part of a human body using hot water,
after a user expels stools.
BACKGROUND ART
[0002] A sanitary washing device includes a heat exchanger for
increasing the temperature of washing water up to a suitable
temperature when a private part of a human body is washed using the
water, after a user expels stools. There are various types of heat
exchangers. One exemplary heat exchanger is a plate type heat
exchanger which is disclosed in Patent Literature 1. This heat
exchanger is configured in such a manner that a heater of a plate
type (plate heater) is stored into a casing of a rectangular
parallelepiped shape with a small width and placed to be oriented
vertically, the heat exchanger having two passages which extend
upwardly and sinuously horizontally along heat transfer surfaces of
the plate heater, respectively. When the plate heater is being
actuated, the washing water is flowed through the passages to raise
its temperature up to a suitable temperature. The heat exchanger
disclosed in Patent Literature 1 has advantages that since the
passages have small flow passage cross-sectional areas, the washing
water can be flowed at a high and uniform speed, a heat transfer
rate can be improved, and its configuration can be made
compact.
CITATION LISTS
Patent Literature
[0003] Patent Literature 1: Japanese Laid-Open Patent Application
Publication No. Hei. 10-220876 (particularly, see FIG. 2)
SUMMARY OF THE INVENTION
Technical Problem
[0004] However, in the above stated conventional heat exchanger,
water flowing into the heat exchanger through a water inlet of the
casing is heated on the surface of the plate heater, when it is
flowing through the passages extending from the water inlet to a
water outlet. The temperature of water flowing in the passages
becomes higher as the water gets closer to the water outlet, and
the water is likely to be locally boiled on the surface of a
portion of the plate heater which is closer to the water outlet. If
a high-temperature portion is formed locally on the surface of a
boundary between the plate heater and the water in this way, scale
is likely to be generated from a calcium component and the like
contained in the washing water flowing in the passages and is
likely to adhere to the surface of the plate heater. On the portion
of the surface of the plate heater of the heat exchanger, to which
the scale is adhering, heat transfer to the water is impeded due to
the scale. This causes a local temperature rise in the surface
temperature of the plate heater, and adhering of the scale onto the
surface progresses. The resulting accumulated scale might increase
a passage resistance, which would make it difficult to ensure a
necessary amount of the washing water. In a case where the plate
heater is a ceramic heater, a crack or a break of the plate heater
might be caused by thermal distortion due to a partial temperature
difference generated due to the scale.
[0005] The conventional plate heat exchanger provided with the
passages extending along the heat transfer surfaces of the plate
heater, is designed on the ground that the amount of heat
transferred to the washing water is substantially equal between one
of the heat transfer surfaces and the other heat transfer surface
in the plate heater. Because of this, if a great difference in the
amount of heat transferred to the water is generated between the
heat transfer surfaces, the washing water in the passage
corresponding to one of the heat transfer surfaces is likely to be
locally boiled and air bubbles are likely to be generated. The
generated air bubbles increase a flow resistance of the washing
water flowing in the passages, and hence a good balance of the
amount of the washing water between the heat transfer surfaces of
the plate heater cannot be maintained, which results in an increase
in the difference in the amount of heat transferred to the water.
In a case where a thermistor which is actuated responsively to the
temperature of the outflowing water is provided in the vicinity of
a water outlet of a heat exchanger, air bubbles grown to a great
size may make it difficult to actuate the thermistor properly.
[0006] If the above air bubbles adhere onto the heat transfer
surface of the plate heater and are grown to a great size between
the heat transfer surface of the plate heater and the washing
water, the heat transfer surface and the washing water get
separated from each other, because of the presence of the air
bubbles. In this case, it becomes difficult to transfer the heat
from the plate heater to the washing water, which significantly
elevates the temperature of the heat transfer surface of the plate
heater. If the temperature of only one heat transfer surface of
plate heater increases significantly, and hence a temperature
difference between the heat transfer surfaces increases,
deformation or the like of the plate heater occurs due to a thermal
stress.
[0007] A dominant factor of the adhesion of the scale to the heat
transfer surface is the temperature of the heat transfer surface.
Typically, a desired temperature of the heat transfer surface is
suitably determined depending on a concentration of the scale of
tap water, a desired endurance time of the heater, etc., that is,
for example, the temperature is not higher than 100 degrees C. at
which the water is boiled, preferably, not higher than 80 degrees
C. If the temperature of even a portion of the heat transfer
surface exceeds the desired temperature, then the scale would
adhere onto that portion and would impede heat transfer, which must
be averted. To avert this, the area of the heat transfer surface
may be possibly increased. This undesirably results in a cost
increase of the heat exchanger. To satisfy a desired temperature of
the heat transfer surface while minimizing the area of the heat
transfer surface of the heat exchanger, it is necessary to
configure the heat exchanger so as to set local distributions of a
watt density of the plate heater or local distributions of a heat
transfer rate so that local temperature distributions of the heat
transfer surface become substantially uniform over the entire heat
transfer surface.
[0008] By increasing the flow speed of the washing water, the heat
transfer rate can be improved and generation of the air bubbles can
be suppressed, or the generated air bubbles can be quickly
discharged to outside through a water outlet. Also, by improving
the heat transfer rate, the area of the heat transfer surface can
be reduced. However, in general, in the heat exchanger for use with
a hot water washing toilet seat, the amount of washing water per
usage is small. Therefore, to increase the flow speed of the
washing water inside the heat exchanger, a passage width is
required to be set very small to ensure the flow speed. Typically,
a maximum value of the flow rate is set to about 500 cc/min. To
increase the flow speed of the heat exchanger in correspondence
with this flow rate, a gap of the passage formed along the heat
transfer surface of the plate heater is required to be set to a
value less than 0.5 mm. However, in this structure, the width of
the passage is extremely small, and therefore the flow speed tends
to become locally non-uniform. Furthermore, as a result of
increasing the flow speed of the washing water inside the heat
exchanger, a pressure loss of the heat exchanger increases. Because
of this, it is difficult to increase the flow speed significantly
in the heat exchanger. In the case of the passage extending
sinuously horizontally as disclosed in Patent Literature 1, a
distance between the water inlet and the water outlet is large.
Therefore, a long time is required to move the air bubbles
generated inside to the water outlet. In addition, because of the
small flow passage cross-sectional area, the washing water tends to
get stagnant due to the generated air bubbles.
[0009] In order to solve the above mentioned problems associated
with the prior arts, an object of the present invention is to
provide a heat exchanger which is capable of suppressing formation
and adhesion of scale and has a longer life, by configuring a plate
heater such that a watt density is lower at a water outlet side
where a water temperature is relatively higher than at a water
inlet side where the water temperature is relatively lower, to make
a temperature of a heat transfer surface uniform and to suppress a
highest surface temperature of the heater. Another object of the
present invention is to provide a heat exchanger capable of
suppressing generation of air bubbles inside thereof, and guiding
the generated air bubbles quickly to the water outlet.
Solution to Problem
[0010] A heat exchanger of the present invention comprise s a
casing having a water inlet and a water outlet; a heater disposed
inside the casing and having surfaces serving as heat transfer
surfaces; and a passage space provided inside the heater, to guide
a fluid which has flowed into the heat exchanger through the water
inlet to the water outlet, the fluid being guided to the water
outlet while exchanging heat with the heat transfer surfaces of the
heater; characterized in that the heater is configured in such a
manner that a heat generation density in a portion closer to the
water outlet is lower than a heat generation density in a portion
closer to the water inlet (Claim 1).
[0011] In accordance with this configuration, the fluid (e.g.,
washing water) which has flowed into the heat exchanger through the
water inlet of the casing is heated by the heat transfer surface of
the heater, and thereby a temperature of the fluid gradually
increases as it is getting closer to the water outlet. The surface
temperature of a portion of the heater which is closer to the water
inlet is likely to rise due to the higher heat generation density
of the heater, but a large amount of heat is taken away from that
portion by the fluid which has not been heated yet and still has a
lower temperature (i.e., a degree of sub-cooling is great).
Therefore, in the portion of the heater closer to the water inlet,
the surface temperature does not rise up to a high temperature at
which local boiling will take place. By comparison, the surface
temperature of a portion of the heater which is closer to the water
outlet tends to become higher as compared to the surface
temperature of the portion of the heater which is closer to the
water inlet, because the fluid contacting the surface of the heater
has already been heated. Heat taken away from the surface of the
heater by the fluid is lessened in amount, and the degree of the
sub-cooling becomes less. However, the heater is configured in such
a manner that the heat generation density is lower in the portion
closer to the water outlet than in the portion closer to the water
inlet. As a result, in the portion of the heater closer to the
water outlet, the surface temperature does not rise up to a high
temperature at which local boiling will take place.
[0012] As described above, since the heater is configured in such a
manner that the heat generation density is lower in the portion
closer to the water outlet than in the portion closer to the water
inlet, the temperature is suppressed from rising up to a high
temperature at which local boiling will take place, even on a
surface of a boundary between the water and the portion of the
heater which is closer to the water outlet where the temperature of
the fluid tends to become higher. Thus, the heat exchanger is
allowed to prevent formation and adhesion of the scale, and have a
longer life. Since the heat generation density is set higher in the
portion of the heater which is closer to the water inlet, where the
temperature of the fluid is relatively lower and the flow speed of
the fluid typically tends to be higher than at the water outlet,
the heat transfer rate in the portion of the heat exchanger in the
vicinity of the water inlet can be improved.
[0013] In the heat exchanger of the present invention, the heater
may be a plate heater placed to be oriented in a direction
substantially parallel to a vertical direction, and may have an
obverse main surface and a reverse main surface which are the heat
transfer surfaces; and the passage space may extend from the water
inlet at a lower portion to the water outlet at an upper portion
along the obverse and reverse heat transfer surfaces of the plate
heater (Claim 2).
[0014] In the case of a normal plate heater in which local
distributions of the heat generation density are uniform over the
entire heat transfer surface, the temperature becomes highest at a
portion of the plate heater which is closer to the water outlet,
and the scale is initially generated on this portion. However, the
heat generation density of the plate heater of the present
invention is set lower in the portion closer to the water outlet
than in the portion closer to the water inlet. Therefore, a heat
flux of the heat exchanger is higher in the portion of the heater
which has a higher heat generation density and is lower in the
portion of the heater which has a lower heat generation density.
This can make the temperature of the heat transfer surface uniform.
As a result, the temperature does not rise up to a high temperature
in a localized portion to an extent that the scale will adhere onto
the localized portion.
[0015] In such a configuration, heat exchange is carried out in
such a manner that the heat is transferred from the plate heater to
the washing water flowing while contacting the obverse and reverse
main surfaces of the plate heater and a heat efficiency is high
without a substantial heat release loss. Since the obverse and
reverse main surfaces of the plate heater are used as the heat
transfer areas, the heat exchanger can be made compact.
[0016] In the heat exchanger of the present invention, the heater
may be a ceramic heater including a ceramic base body, a heat
generation resistive element formed by printing a pattern of a
resistive element on the ceramic base body, and an electrode, and
the printed pattern may have a line width greater in a portion of
the heater which is closer to the water outlet than in a portion of
the heater which is closer to the water inlet (Claim 3).
[0017] In such a configuration, as the line width of the printed
pattern which is a heat generation resistive element increases, an
electric resistance generated by flowing a current is lower and a
heat generation amount decreases. Therefore, it is possible to
provide a ceramic heater configured in such a manner that the heat
generation amount is greater (i.e., heat generation density is
higher) in the portion of the heater which is closer to the water
inlet, in which the line width of the printed pattern is smaller,
while the heat generation amount is smaller (i.e., heat generation
density is lower) in the portion of the heater which is closer to
the water outlet, in which the line width of the printed pattern is
greater. Because of this structure, it is possible to suppress the
temperature from rising up to a high temperature at which local
boiling will take place, on the surface of the boundary between the
fluid and the portion of the ceramic heater which is closer to
water outlet where the temperature of the fluid tends to be higher,
and possible to prevent formation and adhesion of the scale. As a
result, a heat exchanger constituted by ceramic which has a smaller
heat capacity, but tends to get more easily cracked, as compared to
metal materials, can prevent a crack and have a longer life while
maintaining a high heat exchange efficiency.
[0018] In the heat exchanger of the present invention, the heater
may be a ceramic heater including a ceramic base body, a heat
generation resistive element formed by printing a pattern of a
resistive element on the ceramic base body, and an electrode, and
the printed pattern may have a line interval (in-line gap) greater
in a portion of the heater which is closer to the water outlet than
in a portion of the heater which is closer to the water inlet
(Claim 4).
[0019] In such a configuration, it is possible to provide a ceramic
heater configured in such a manner that the heat generation amount
is greater (i.e., heat generation density is higher), in the
portion closer to the water inlet in which the line interval of the
printed pattern is smaller, while the heat generation amount is
smaller (i.e., heat generation density is lower), in the portion
closer to the water outlet in which the line interval of the
printed pattern is greater. Because of the above stated reason, it
is possible to achieve a heat exchanger which can prevent formation
and adhesion of the scale, prevent a crack of the ceramic heater,
and have a longer life.
[0020] In the heat exchanger of the present invention, the passage
space may include an upstream space including an opening of the
water inlet and a downstream space including an opening of the
water outlet, and a throttle passage having a smaller flow passage
cross-sectional area than another space may be provided between the
upstream space and the downstream space (Claim 5).
[0021] In such a configuration, when the fluid is flowing from the
upstream space toward the downstream space, the flow speed of the
fluid becomes a highest speed just after the fluid has exited the
throttle passage, and thereafter gradually decreases. Because of
this, the heat transfer rate on the heat transfer surface
associated with this throttle passage tends to be highest when the
flow speed of the fluid becomes the highest speed just after the
fluid has exited the throttle passage, and then be gradually
lowered. As compared to a heat transfer rate provided only by a
normal natural convection, the value of the heat transfer rate
increases significantly. Therefore, the rate of heat transfer from
the plate heater to the fluid in the downstream space can be
improved, and the air bubbles can be guided to the water outlet
quickly along with the fluid flowing at a high speed through the
throttle passage.
[0022] In the heat exchanger of the present invention, the passage
space at one heat transfer surface side of the plate heater and the
passage space at the other heat transfer surface side of the plate
heater may be symmetric (Claim 6).
[0023] In such a configuration, a balance of a heat transfer amount
of the heat transfer surfaces of the heater can be ensured, and
deformation of the heater due to a thermal stress can be
prevented.
[0024] In the present invention, the state where "two passage
spaces at one heat transfer surface side of the plate heater and at
the other heat transfer surface side of the plate heater are
symmetric" refers to a state in which the plate heater is disposed
between the two passage spaces and the two passage spaces are
disposed to face each other to be substantially plane-symmetric
with respect the heat transfer surface (at least one of the two
heat transfer surfaces) of the plate heater." A specific example of
this is, for example, a positional relationship between two passage
spaces 25 disposed to face each other to be plane-symmetric with
respect to a heat transfer surface (first transfer surface 20a or
second heat transfer surface 20b), as shown in FIGS. 2 and 3 as
described later.
[0025] In the heat exchanger of the present invention, the
downstream space may have a greater volume than the upstream space
(Claim 7).
[0026] In such a configuration, since the flow speed of the fluid
can be increased in the downstream space having a greater volume,
the heat transfer rate can be further improved.
[0027] In the heat exchanger of the present invention, the throttle
passage may have a horizontal throttle passage extending
substantially horizontally from a portion of the heat exchanger
which is closer to the water inlet, to flow the fluid in an upward
direction toward the downstream space (Claim 8).
[0028] In such a configuration, the fluid which has passed through
the horizontal throttle passage migrates upward as in the case
where the fluid which has been heated up by the heater and has a
relatively high temperature migrates upward by a natural
convection. Since the fluid which has passed through the horizontal
throttle passage migrates upward as in the case of the natural
convection, in this way, the flow speed of the fluid can be further
improved.
[0029] In the heat exchanger of the present invention, the throttle
passage may have a vertical throttle passage extending
substantially vertically upward, from one end portion of the
horizontal throttle passage which is farther from the water inlet
than the other end portion of the horizontal throttle passage, to
flow the fluid horizontally toward the downstream space (Claim
9).
[0030] In such a configuration, the fluid which has passed through
the vertical throttle passage is mixed with the fluid which has
passed through the horizontal throttle passage to generate a
disordered flow, which allows the fluid to be agitated. As a
result, the heat transfer rate can be improved.
[0031] In the heat exchanger of the present invention, the throttle
passage may have a slit shape; and the throttle passage may have an
increased-width portion having a greater opening width than another
portion (Claim 10).
[0032] In such a configuration, a difference is generated between
flow speed of the fluid which has passed through the
increased-width portion of the throttle passage and the flow speed
of the fluid which has passed through a portion of the throttle
passage which is other than the increased-width portion. When the
fluids flow into the downstream space at different flow speeds,
they form a disordered flow and agitate the fluid in the downstream
space, so that the heat transfer rate can be improved.
[0033] In the heat exchanger of the present invention, an agitating
wall for agitating the fluid may be provided in the downstream
space to extend in a substantially upward and downward direction
along the plate heater; and the agitating wall may be corrugated to
have a horizontal amplitude (Claim 11).
[0034] In such a configuration, since the fluid in the downstream
space is further agitated by the agitating walls, the heat transfer
rate can be further improved. In addition, since the agitating
walls extend in the upward and downward direction, the generated
air bubbles can migrate upward quickly to the water outlet, by a
buoyancy force, and are discharged therethrough, without being
impeded.
[0035] In the heat exchanger of the present invention, a buffer
wall extending substantially horizontally along the plate heater
may be provided in the downstream space (Claim 12).
[0036] In such a configuration, the fluid flowing through the
downstream space is held back just before each buffer wall and is
diffused when it is passing through a narrow space between the
buffer wall and the plate heater. By agitating the fluid in this
way, the heat transfer rate can be improved.
[0037] In the heat exchanger of the present invention, the buffer
wall has a plurality of buffer walls arranged in the upward and
downward direction; and the buffer walls are provided with
remaining portions formed (left) by cutting portions of the buffer
walls such that positions of the remaining portions are different
between adjacent upper and lower buffer walls when viewed from
above (Claim 13).
[0038] In such a configuration, since the space between the
remaining portion of the buffer wall and the plate heater has a
great flow passage cross-sectional area, a part of the fluid is
likely to migrate substantially horizontally toward the remaining
portion. Therefore, in the downstream space, a water flow migrating
substantially horizontally toward the remaining portion and a water
flow migrating vertically upward beyond the buffer wall are mixed
and formed into a disordered flow, which allows the fluid to be
agitated. As a result, the heat transfer rate can be improved.
[0039] The heat exchanger of the present invention comprises a pair
of passage forming members disposed to sandwich the plate heater;
each of the passage forming members may include a base portion of a
plate shape disposed to face the plate heater, and a rib protruding
from a surface of the base portion which faces the plate heater;
and the slit-shape throttle passage may be defined by the rib and
the plate heater which faces the rib and provided between the rib
and the plate heater which faces the rib (Claim 14).
[0040] In such a configuration, a heat exchanger including a
throttle passage with a relatively simple configuration can be
provided.
[0041] In the heat exchanger of the present invention, the heater
may be a plate heater placed to be oriented in a direction
substantially parallel to a vertical direction, and has an obverse
main surface and a reverse main surface which are the heat transfer
surfaces; and the passage space may be formed in a sinuous passage
extending from the water inlet at a lower portion to the water
outlet at an upper portion along the obverse and reverse heat
transfer surfaces of the plate heater (Claim 15).
[0042] In such a configuration, heat exchange is carried out in
such a manner that the heat is transferred from the plate heater to
the washing water flowing while contacting the obverse and reverse
main surfaces of the plate heater and a heat efficiency is high
without a substantial heat release loss. Since the obverse and
reverse main surfaces of the plate heater are used as the heat
transfer areas, the heat exchanger can be made compact. Since the
sinuous passage can provide an increased passage length and a
higher flow speed of the fluid, a layer (temperature boundary
layer) of the fluid to which heat is substantially transferred from
the surface of the heater is thinned. Therefore, the heat transfer
rate is improved, and the temperature of the surface of the heater
is lowered. Thus, local boiling can be suppressed more effectively,
and hence formation and adhesion of the scale can be prevented more
effectively.
[0043] In the heat exchanger of the present invention, wherein the
sinuous passage may be defined by a plurality of wall portions
arranged vertically to extend substantially horizontally, and the
sinuous passage may have in a range from the water inlet to the
water outlet, a passage for guiding the fluid in one direction in a
substantially horizontal direction, and a passage for guiding the
fluid in an opposite direction in the substantially horizontal
direction such that the passages are arranged alternately from a
lower side to an upper side; and a bypass passage is provided in an
upward and downward direction on a portion of each of the wall
portions in a longitudinal direction thereof to provide
communication between adjacent upper and lower passages (Claim
16).
[0044] In such a configuration, the air bubbles can be guided
quickly to the water outlet through the bypass passages formed in
an upward and downward direction in the sinuous passage while
improving the heat transfer rate by the high-speed flow of the
washing water. In other words, since the sinuous passage makes the
flow passage cross-sectional area smaller, the flow speed of the
washing water can be made high and uniform. As described above, the
heater is configured in such a manner that the heat generation
density is lower in the portion closer to the water outlet than in
the portion closer to the water inlet, the temperature of a portion
of the heat transfer surface is prevented from rising up to a high
temperature at which local boiling of the washing water will take
place, and generation of the air bubbles is suppressed. If the air
bubbles are generated, the generated air bubbles are allowed to
migrate quickly to the water outlet through the bypass passage
having a shorter length than the overall sinuous passage. This
makes it possible to prevent an event in which a passage resistance
at one heat transfer surface side becomes higher than that at the
other heat transfer surface side, or the temperature of one heat
transfer surface becomes much higher than that of the other heat
transfer surface, due to the air bubbles. Thus, local boiling which
would lead to formation and adhesion of the scale can be further
suppressed. Since the air bubbles generated on the surface of the
heater migrate through the bypass passages and are discharged
quickly through the water outlet, the air bubbles are prevented
from growing to a great size. Thus, a problem that the operation of
a thermistor located in the vicinity of the water outlet is impeded
due to the air bubbles with a great size, will not occur.
[0045] In the heat exchanger of the present invention, the sinuous
passage at one heat transfer surface side of the plate heater and
the sinuous passage at the other heat transfer surface side of the
plate heater may be symmetric, and the bypass passage at one heat
transfer surface side of the plate heater and the bypass passage at
the other heat transfer surface side of the plate heater may be
symmetric (Claim 17).
[0046] In such a configuration, in addition to the above
advantages, a balance of a heat transfer amount between the obverse
and reverse heat transfer surfaces of the heater is properly
maintained, and deformation of the heater due to a thermal stress
can be prevented.
[0047] In the present invention, the state where "two sinuous
passages at one heat transfer surface side of the plate heater and
at the other heat transfer surface side of the plate heater are
symmetric" refers to a state in which the plate heater is disposed
between the two sinuous passage spaces and the two sinuous passage
spaces are disposed to face each other to be substantially
plane-symmetric with respect the heat transfer surface (at least
one of the two heat transfer surfaces) of the plate heater." A
specific example of this is, for example, a positional relationship
between two sinuous passages (sinuous passage 135 and sinuous
passage 145) disposed to face each other to be substantially
plane-symmetric with respect to a heat transfer surface (first
transfer surface 120a or second heat transfer surface 120b), as
shown in FIGS. 15 and 16 as described later.
[0048] In the present invention, the state where "two bypass
passages at one heat transfer surface side of the plate heater and
at the other heat transfer surface side of the plate heater are
symmetric" refers to a state in which the plate heater is disposed
between the two bypass passages and the two sinuous passages are
disposed to face each other to be substantially plane-symmetric
with respect the heat transfer surface (at least one of the two
heat transfer surfaces) of the plate heater."
[0049] In the heat exchanger of the present invention, bypass
passages formed on the plurality of wall portions may substantially
conform in position to each other when viewed from above (Claim
18).
[0050] In such a configuration, in addition to the above
advantages, the air bubbles can migrate straightly upward through
the bypass passages and reach the water outlet quickly.
[0051] The heat exchanger of the present invention may comprise a
pair of passage forming members disposed to sandwich the plate
heater; and each of the passage forming members may include a base
portion of a plate shape disposed to face the plate heater, and a
plurality of ribs protruding from a surface of the base portion
which faces the plate heater to form the wall portions; and a
remaining portion formed by cutting a portion of each of the
plurality of ribs may be provided on a portion of each of the
plurality of ribs in a longitudinal direction thereof such that a
tip end of the rib is dented with respect to another portion to
form the bypass passage (Claim 19).
[0052] In such a configuration, in addition to the above
advantages, the bypass passages can be formed by cutting portions
of tip ends of the ribs in a heat exchanger including a plate
heater and a pair of passage forming members.
[0053] In the heat exchanger of the present invention, the
remaining portion of the rib may have a tapered shape when viewed
from above such that a cut portion width of the remaining portion
decreases as a cut portion depth of the remaining portion increases
(Claim 20).
[0054] In the heat exchanger of the present invention, the
remaining portion of the rib may have a circular-arc shape when
viewed from above such that a cut portion depth of a center portion
of a cut portion width is great (Claim 21).
[0055] In such a configuration, in addition to the above
advantages, air bubbles having a great diameter can pass through
the remaining portions (bypass passages).
[0056] In the heat exchanger of the present invention, the
remaining portion of the rib provided at a relatively upper side
may have a greater cut portion width than the remaining portion of
the rib provided at a relatively lower side (Claim 22).
[0057] In such a configuration, in addition to the above
advantages, the flow speed can be increased by reducing the cut
portion width of the remaining portion, because the water
temperature is not sufficiently high and the air bubbles are less
likely to be generated in a lower region (i.e., upstream side). In
contrast, in an upper region (i.e., downstream side) where the
water temperature tends to be high, the air bubbles are allowed to
surely pass through the remaining portion by setting the cut
portion width of the remaining portion greater.
[0058] The heat exchanger of the present invention, the remaining
portion may not be provided on the rib provided at a relatively
lower side; and the remaining portion may be provided on the rib
provided at a relatively upper side (Claim 23).
[0059] In such a configuration, in addition to the above
advantages, the flow speed can be further increased without
providing the remaining portion in the lower region where the air
bubbles are less likely to be generated, while the air bubbles are
allowed to surely pass through the remaining portion provided in
the upper region where the air bubbles are easily generated.
ADVANTAGEOUS EFFECTS OF THE INVENTION
[0060] In accordance with the present invention, it is possible to
provide a heat exchanger which is capable of suppressing a
temperature from rising up to a high temperature at which local
boiling will take place, suppressing generation of air bubbles
inside thereof, preventing formation and adhesion of scale, and
having a longer life, while improving a heat transfer rate. Also,
it is possible to provide a heat exchanger which is capable of
suppressing generation of air bubbles inside passages, and guiding
the generated air bubbles quickly to a water outlet.
BRIEF DESCRIPTION OF THE DRAWINGS
[0061] FIG. 1 is a perspective view showing an external appearance
of a sanitary washing device including a heat exchanger according
to an embodiment of the present invention.
[0062] FIG. 2 is a front view showing a configuration of an
external appearance of a heat exchanger according to Embodiment
1.
[0063] FIG. 3 is a cross-sectional view of the heat exchanger taken
along B-B of FIG. 2.
[0064] FIG. 4 is a plan view showing an example of a pattern of a
resistive element formed on a plate heater of the heat exchanger of
FIG. 3.
[0065] FIG. 5 is a plan view showing another example of the pattern
of the resistive element formed on the plate heater of the heat
exchanger of FIG. 3.
[0066] FIG. 6 is an exploded view of the heat exchanger. FIG. 6(a)
is a plan view of the heat exchanger in a state where a second
passage forming member and the plate heater are removed, when
viewed from a base surface side of a first passage forming member,
and FIG. 6(b) is a plan view showing the second passage forming
member when viewed from a base surface side thereof.
[0067] FIG. 7 shows a configuration of a region near ribs in an
assembled heat exchanger along a direction of X, to shown a
configuration of throttle passages. FIG. 7(a) is an enlarged view
of a portion VIIa of FIG. 3, and FIG. 7(b) is an enlarged view
showing a modified example of throttle passages.
[0068] FIG. 8 is a view showing a configuration of a heat exchanger
according to Embodiment 2. FIG. 8(a) is a plan view of the heat
exchanger in a state where a second passage forming member is
removed, when viewed from a base surface side of a first passage
forming member, and FIG. 8(b) is a plan view showing an example of
a flow of washing water.
[0069] FIG. 9 is a view showing a configuration of a heat exchanger
according to Embodiment 3. FIG. 9(a) is a plan view of the heat
exchanger in a state where a second passage forming member is
removed, when viewed from a base surface side of a first passage
forming member, and FIG. 9(b) is a plan view showing an example of
a flow of washing water.
[0070] FIG. 10 is a view showing a configuration of a heat
exchanger according to Embodiment 4. FIG. 10(a) is a plan view of
the heat exchanger in a state where a second passage forming member
is removed, when viewed from a base surface side of a first passage
forming member, and FIG. 10(b) is a plan view showing an example of
a flow of washing water.
[0071] FIG. 11 is a view showing a configuration of a heat
exchanger according to Embodiment 5. FIG. 11(a) is a plan view of
the heat exchanger in a state where a second passage forming member
is removed, when viewed from a base surface side of a first passage
forming member. FIG. 11(b) is a cross-sectional view of the heat
exchanger taken along B-B. FIG. 11(c) is a cross-sectional view of
the heat exchanger taken along C-C.
[0072] FIG. 12 is a view showing a configuration of a heat
exchanger according to Embodiment 6. FIG. 12(a) is a plan view of
the heat exchanger in a state where a second passage forming member
is removed, when viewed from a base surface side of a first passage
forming member. FIG. 12(b) is a cross-sectional view of the heat
exchanger taken along B-B.
[0073] FIG. 13 is a view showing a configuration of a heat
exchanger according to Embodiment 7. FIG. 13(a) is a plan view of
the heat exchanger in a state where a second passage forming member
is removed, when viewed from a base surface side of a first passage
forming member. FIG. 13(b) is a cross-sectional view of the heat
exchanger taken along B-B.
[0074] FIG. 14 is a view showing a modified example of the heat
exchanger of Embodiment 1 and showing the heat exchanger in a state
where a second passage forming member and a plate heater are
removed, when viewed from a base surface side of a first passage
forming member.
[0075] FIG. 15 is a front view showing a configuration of a heat
exchanger according to Embodiment 8. FIG. 15(a) is a front view
showing a configuration of an external appearance of the heat
exchanger. FIG. 15(b) is a cross-sectional view of the heat
exchanger taken along B-B.
[0076] FIG. 16 is an exploded view of the heat exchanger. FIG.
16(a) is a plan view of the heat exchanger in a state where a
second passage forming member and a heater are removed, when viewed
from a base surface side of a first passage forming member, and
FIG. 6(b) is a plan view showing the second passage forming member
when viewed from a base surface side thereof.
[0077] FIG. 17 is a cross-sectional view of the heat exchanger,
taken along XVII-XVII of FIG. 16.
[0078] FIG. 18 is a view showing a configuration of a rib and a
remaining portion. FIG. 18(a) is an enlarged view of a portion
XVIIIa of FIG. 17 to show a configuration of the remaining portion
taken along Z-direction. FIG. 18(b) is an enlarged view of a
portion XVIIIb of FIG. 15 to show a configuration of the remaining
portion taken along X-direction.
[0079] FIG. 19 is a view showing a flow of washing water and air
bubbles in the heat exchanger of Embodiment 8, and is a plan view
showing a configuration of the heat exchanger when viewed from a
base surface side of a first passage forming member.
[0080] FIG. 20 is an enlarged view of a remaining portion taken
along Z-direction, to show another configuration of the remaining
portion. FIG. 20(a) is an enlarged view showing a remaining portion
having a tapered deepest portion. FIG. 20(b) is an enlarged view
showing a remaining portion having a circular-arc deepest portion.
FIG. 20(c) is an enlarged view showing a remaining portion having a
deepest portion defined by a tilted surface.
[0081] FIG. 21 is a view showing a configuration of a heat
exchanger according to Embodiment 10, and is a plan view showing
the heat exchanger when viewed from a base surface side of a first
passage forming member.
[0082] FIG. 22 is a view showing a configuration of a heat
exchanger according to Embodiment 11, and is a plan view showing
the heat exchanger when viewed from a base surface side of a first
passage forming member.
DESCRIPTION OF THE EMBODIMENTS
[0083] Hereinafter, a heat exchanger according to an embodiment of
the present invention will be described with reference to the
drawings, using an example in which the heat exchanger is
incorporated into a sanitary washing device. The present invention
is not limited to the embodiment.
[0084] [Sanitary Washing Device]
[0085] FIG. 1 is a perspective view showing an external appearance
of a sanitary washing device including a heat exchanger according
to an embodiment of the present invention. As shown in FIG. 1, a
sanitary washing device 1 is provided on the upper surface of a
toilet bowl 2, and includes a base portion 3, a toilet seat 4, a
toilet cover 5, an operating unit 6, and others. The base portion 3
is disposed behind the toilet seat 4 (behind from the perspective
of a user seated). In the interior of a casing 3a which is
elongated in a lateral direction and hollow, a washing unit (not
shown), a drying unit (not shown), a control unit (not shown) for
controlling the operation of these units, a heat exchanger 10
(indicated by a broken line) according to the present embodiment,
etc., are stored. Into the heat exchanger 10, tap water (fluid,
liquid, washing water) is introduced from water utilities
incorporated in a building structure attached with the toilet bowl
2, and is warmed up to a suitable temperature inside thereof. When
the user operates the operating unit 6 to input a predetermined
command, the washing unit is actuated to eject the washing water to
a private part of a human body in the form of a shower from a
nozzle included in the washing unit.
Embodiment 1
[Heat Exchanger]
[0086] FIGS. 2 and 3 show a configuration of the heat exchanger 10
(10A). FIG. 2 is a front view showing an external appearance of the
heat exchanger 10 (10A). FIG. 3 is a cross-sectional view of the
heat exchanger 10 (10A) taken along B-B of FIG. 2. As shown in
FIGS. 2 and 3, in its external appearance, the heat exchanger 10A
is formed by a flat plate having a small thickness and having a
rectangular shape as viewed from front. As shown in FIG. 3, the
heat exchanger 10A includes a plate heater 20 of a rectangular
plate shape, a first passage forming member 21 disposed to face one
surface (first heat transfer surface) 20a, a second passage forming
member 22 disposed to face the other surface (second heat transfer
surface) 20b, and a casing 23 accommodating the plate heater 20,
the first passage forming member 21 and the second passage forming
member 22, and having a water inlet 23a and a water outlet 23b. The
plate heater 20 is made of ceramic, while the first passage forming
member 21 and the second passage forming member 22, are made of
reinforced ABS resin formed by compounding glass fiber into ABS
resin.
[0087] Hereinafter, a description will be given of a state where
the heat exchanger 10A is placed to be oriented vertically such
that the heat transfer surfaces of the plate heater 20 are parallel
to a vertical direction, except for cases specially noted. As shown
in FIG. 2, the vertical direction is Z-direction, a direction
perpendicular to Z-direction and parallel to the heat transfer
surfaces of the plate heater 20 is X-direction, and a direction
(direction perpendicular to the first heat transfer surface 20a)
perpendicular to these two directions is Y-direction.
[0088] As shown in FIG. 3, the first passage forming member 21
includes a base portion 30 of a rectangular plate shape which faces
the first heat transfer surface 20a, and a rib 31 protruding from a
surface (base surface) 30a of the base portion 30 which faces the
first heat transfer surface 20a. Likewise, the second passage
forming member 22 includes a base portion 40 of a rectangular plate
shape which faces the second heat transfer surface 20b, and a rib
41 protruding from a surface (base surface) 40a of the base portion
40 which faces the second heat transfer surface 20b.
[0089] A wall-like flange portion 32 is provided to extend along
the peripheral edge portion of the base portion 30 of the first
passage forming member 21. The flange portion 32 is extended by a
predetermined dimension toward the second passage forming member
22. An engagement groove 33 is formed at the tip end portion of the
flange portion 32 so as to extend along the periphery of the flange
portion 32. A wall-like flange portion 42 is provided to extend
along the peripheral edge portion of the base portion 40 of the
second passage forming member 22. The flange portion 42 is extended
by a predetermined dimension away from the first passage forming
member 21. The tip end portion of the flange portion 42 is bent
back toward the first passage forming member 21. An engagement
projection 43 is formed at the tip end portion of the flange
portion 42 so as to extend along the periphery of the flange
portion 42.
[0090] The first passage forming member 21 is externally fitted to
the second passage forming member 22 such that the base surface 30a
faces the base surface 40a. To be more specific, the flange portion
32 of the first passage forming member 21 is externally fitted to
the flange portion 42 of the second passage forming member 22, and
the engagement projection 43 of the second passage forming member
22 is fitted into the engagement groove 33 of the first passage
forming member 21 (e.g., the engagement projection 43 is secured to
the engagement groove 33 by ultrasonic fusion-bonding.) This allows
the first passage forming member 21 and the second passage forming
member 22 to be joined together in a sealed state, thereby forming
a passage space 25 inside the first passage forming member 21 and
the second passage forming member 22.
[0091] As shown in FIGS. 2 and 3, the water inlet 23a is provided
at the lower portion of one end portion of the casing 23 in
X-direction, while the water outlet 23b is provided at the upper
portion of one end portion of the casing 23 in X-direction. As
shown in FIG. 3, the water inlet 23a and the water outlet 23b
communicate with the passage space 25.
[0092] FIG. 4 is a plan view showing an example of a pattern of a
resistive element formed on the plate heater 20 of the heat
exchanger of FIG. 3. As shown in FIG. 4, the plate heater 20 is
configured in such a manner that a resistive element (heater line)
pattern 20p is printed on a ceramic base body 20k. The resistive
element pattern 20p is configured in such a manner that a heater
line width 20s is smaller in a portion of the plate heater 20 which
is closer to the water inlet 23a and is greater in a portion of the
plate heater 20 which is closer to water outlet 23b. In brief,
according to the resistive element pattern 20p, the heater line
width 20s is smaller and a resistance value is higher in the
portion of the plate heater 20 which is closer to water inlet 23a,
while the heater line width 20s is greater and a resistance value
is lower in the portion of the plate heater 20 which is closer to
water outlet 23b. In other words, the plate heater 20 is configured
in such a manner that a heat generation density is lower in the
portion closer to the water outlet 23b than in the portion closer
to the water inlet 23a.
[0093] FIG. 5 is a plan view showing another example of the pattern
of the resistive element formed on the plate heater 20 of the heat
exchanger of FIG. 3. Like the resistive element (heater line)
pattern 20p of FIG. 4, the resistive element (heater line) pattern
20p is printed on the ceramic base body 20k in the plate heater 20.
By comparison, the resistive element pattern 20b of FIG. 5 is
configured in such a manner that a heater line interval 20h between
adjacent heater lines is smaller in a portion of the plate heater
20 which is closer to water inlet 23a and is greater in a portion
of the plate heater 20 which is closer to water outlet 23b. That
is, the plate heater 20 is configured in such a manner that the
heater line interval 20h is smaller and a heat generation density
is higher in the portion closer to the water inlet 23a, while the
heater line interval 20h is greater and a heat generation density
is lower in the portion closer to the water outlet 23b.
[0094] The configuration of the plate heater 20 including the
resistive element pattern 20p, shown in FIGS. 4 and 5, is similar
to those of plate heaters 20 of heat exchangers of Embodiments
2.about.7 as described later, and those of plate heaters 120 of
heat exchangers of Embodiments 8.about.11 as described later, as
well as Embodiment 1.
[0095] FIG. 6 is an exploded view of the heat exchanger 10A. FIG.
6(a) shows the heat exchanger 10A in a state where the second
passage forming member 22 and the plate heater 20 are removed, when
viewed from the base surface 30a side of the first passage forming
member 21, and FIG. 6(b) shows the second passage forming member 22
when viewed from the base surface 40a side thereof. As shown in
FIG. 6(a), a single rib 31 is provided on the base surface 30a of
the base portion 30 of the first passage forming member 21 to
extend substantially horizontally (in X-direction).
[0096] To be more specific, one end portion 31a of the rib 31 in
X-direction is located in the vicinity of a region above an opening
of the water inlet 23a at the passage space side, and is in contact
with the inner wall surface of one end portion of the flange
portion 32 in X-direction. The rib 31 extends along X-direction
from one end portion 31a in X-direction on the base surface 30a,
and an opposite end portion 31b thereof in X-direction is in
contact with the inner wall surface of an opposite end portion of
the flange portion 32 in X-direction.
[0097] As shown in FIG. 6(b), a single rib 41 is provided on the
base surface 40a of the base portion 40 of the second passage
forming member 22 to extend substantially horizontally (in
X-direction). The first passage forming member 21 and the second
passage forming member 22 are symmetric with respect to the ribs 31
and 41. To be specific, like the rib 31, the rib 41 is configured
in such a manner that one end portion 41a in X-direction is in the
vicinity of a region above the water inlet 23a, and is in contact
with the inner wall surface of one end portion of the flange
portion 32 in X-direction, in a state where the passage forming
members 21 and 22 are joined together. The rib 41 extends along
X-direction from one end portion 41a in X-direction on the base
surface 40a, and an opposite end portion 41b thereof in X-direction
is in contact with the inner wall surface of an opposite end
portion of the flange portion 32 in X-direction, in a state where
the passage forming members 21 and 22 are joined together.
[0098] The above stated ribs 31 and 41 separates the passage space
25 into an upstream space 25a located at the relatively lower side
and a downstream space 25b located at the relatively upper side. As
shown in FIG. 3, in addition to FIG. 6, the water inlet 23a opens
in the upstream space 25a, while the water outlet 23b opens in the
downstream space 25b. The downstream space 25b has a greater volume
than the upstream space 25a. Since the passage forming members 21
and 22 are joined together such that the plate heater 20 is
sandwiched therebetween, each of the upstream space 25a and the
downstream space 25b is separated into a space at the first heat
transfer surface 20a side and a space at the second heat transfer
surface 20b side with respect to the plate heater 20 located at the
center in a thickness direction (Y-direction) thereof (see FIG.
3).
[0099] The ribs 31 and 41 form throttle passages (horizontal
throttle passages) 37 and 47, respectively, which are smaller in
flow passage cross-sectional area than the upstream space 25a and
the downstream space 25b. FIG. 7 shows a configuration of a region
closer to the ribs 31 and 41 in the assembled heat exchanger 10A
along X-direction. FIG. 7(a) is an enlarged view of a portion VIIa
of FIG. 3, and FIG. 7(b) shows a modified example of the throttle
passages 37 and 47.
[0100] As shown in FIG. 7(a), the ribs 31 and 41 of Embodiment 1
have end surfaces 50 at tip end portions thereof (end portions in
Y-direction which are closer to the plate heater 20), which are not
parallel to the heat transfer surfaces 20a and 20b, respectively.
That is, the end surfaces 50 of the ribs 31 and 41 are tilted
surfaces which are open upward. To be more specific, the end
surfaces 50 are tilted at a predetermined angle A and their upper
portions are more distant from the heat transfer surfaces 20a and
20b, respectively, than their lower portions. Because of this, the
tip end portion of the rib 31 has a triangular shape in which its
lower portion has a tip portion 51 protruding in an acute angle
form. The tip end of the tip portion 51 of the rib 31 and the tip
end of the tip portion 51 of the rib 41 are distant a predetermined
dimension D1 from the heat transfer surfaces 20a and 20b of the
plate heater 20, respectively.
[0101] Between the rib 31 and the heat transfer surface 20a of
plate heater 20, the throttle passage 37 which has an opening width
D1 and has a slit shape is provided, while between the rib 41 and
the heat transfer surface 20b of plate heater 20, the throttle
passage 47 which has an opening width D1 and has a slit shape is
provided. The upstream space 25a of the heat exchanger 10A of the
present embodiment is a closed space, except for the water inlet
23a and the throttle passages 37 and 47. The downstream space 25b
of the heat exchanger 10A of the present embodiment is a closed
space, except for the water outlet 23b and the throttle passages 37
and 47. Therefore, the upstream space 25a communicates with the
downstream space 25b only via the throttle passages 37 and 47
having the small opening width D1.
[0102] Subsequently, the flow of the washing water inside the above
heat exchanger 10A will be described. As shown in FIG. 6(a), the
washing water is introduced into the passage space 25 of the heat
exchanger 10A through the water inlet 23a, and enters the upstream
passage 25a. The upstream space 25a serves to make a pressure
uniform to allow the washing water to flow into the downstream
space 25b uniformly. Since the upstream space 25a is a closed
space, except for the water inlet 23a and the throttle passages 37
and 47, as described above, the washing water in the upstream space
25a generates a relatively high inner pressure. Since the
high-pressure washing water flows into the downstream space 25b
through the throttle passages 37 and 47, the flow speed of the
washing water in the downstream space 25b can be increased.
[0103] The flow speed pattern of the washing water in the
downstream space 25b in this case is schematically indicated by
reference symbols V1, V2, and V3 in FIG. 3. As shown in FIG. 3, the
flow speed pattern of the washing water which has just exited the
throttle passages 37 and 47 is a flow speed pattern indicated by
V1, in which the flow speed is higher particularly in a region
closer to surface of the plate heater 20. The flow speed pattern is
changed into a flow speed pattern (flow speed pattern in which a
highest speed portion is getting closer to an intermediate position
between the second heat transfer surface 20b and the base surface
40a) in which the flow speed is gradually averaged as it is closer
to the water outlet 23b, as indicated by V2 and V3. In any region
of the downstream spaces 25b sandwiching the plate heater 20, the
similar flow speed pattern is formed. In the above described
manner, since the flow speed pattern of the washing water which has
just exited the throttle passages 37 and 47 is the flow speed
pattern indicated by V1, a rate of heat transfer from the heat
transfer surfaces 20a and 20b of the plate heater can be improved.
Furthermore, since the flow speed near the surface of the heater
gradually decreases in a direction from the water inlet 23a toward
the water outlet 23b, the heat transfer rate is higher at the water
inlet 23a side and is lower at the water outlet 23b side.
[0104] The direction of the flow by the above forced convection in
the downstream space 25b (i.e., flow of the washing water which has
passed through the throttle passages 37 and 47 and migrates upward
toward the downstream space 25b) is the same as that of the flow of
the washing water by natural convection which is generated by
heating of the plate heater 20. These two flows enhance the flow
speed, thereby further improving the heat transfer rate.
[0105] As shown in FIG. 7(a), since the tip end portion of the rib
31 and the tip end portion of the rib 41 have the tip portions 51
protruding in the acute angle form at their lower portions,
respectively, the washing water which has just exited the throttle
passages 37 and 47 collides with the washing water in the
downstream space 25b, for example, thereby generating a disordered
flow. By generating the disturbed flow of the washing water in the
downstream space 25b, the washing water can be agitated. Thus, the
rate of heat transfer from the heat transfer surfaces 20a and 20b
of the plate heater 20 can be improved.
[0106] When the water is flowing from the upstream space 25a into
the downstream space 25b, its flow is narrowed rapidly, so that the
water flows into the downstream space 25b in a state where it is
smaller in dimension than a space between the plate heater 20 and
the tip portion 51. Because of this, the flow speed is further
increased, and the heat transfer rate can be improved.
[0107] As described above with reference to FIGS. 4 and 5, the
plate heater 20 is configured in such a manner that the heat
generation density is lower in the portion closer to the water
outlet 23b than in the portion closer to the water inlet 23a, and
the flow speed of the washing water flowing while contacting the
heat transfer surfaces 20a and 20b of the plate heater 20 is
increased by the presence of the throttle passages 37 and 47
provided in the passage space 25, in the portion closer to the
water inlet 23a. This allows a great amount of heat to be
transferred efficiently to the washing water in the portion closer
to the water inlet 23a, where the washing water having a relatively
low temperature flows, while excess heat is prevented from being
transferred to the washing water in the portion closer to the water
outlet 23b, where the washing water having a relatively high
temperature flows. As a result, a heat generation distribution of
the plate heater 20 can be made compatible with a heat exchange
efficiency distribution, and local boiling on the surface of the
plate heater 20 and the resulting generation of air bubbles are
suppressed.
[0108] Since the downstream space 25b including the water outlet
23b is formed as a relatively wide space in which there is no
obstacle, air bubbles can migrate upward toward the water outlet
23b along with the water flow, by a buoyancy force, if the air
bubbles are generated. Therefore, even in a case where the air
bubbles are generated, they can be discharged to outside quickly.
Thus, the heat exchanger 10A of the present embodiment can improve
a heat transfer rate while accomplishing quick discharging of the
air bubbles.
[0109] Although in the present embodiment, the throttle passages 37
and 47 have the shape shown in FIG. 7(a), the present invention is
not limited to this. For example, a structure shown in FIG. 7(b)
may be used.
[0110] To be more specific, as shown in FIG. 7(b), end surfaces 54
of the tip end portions (end portions in Y-direction which are
closer to the plate heater 20) of the ribs 31 and 41 are not
parallel to the heat transfer surfaces 20a and 20b of the plate
heater 20, respectively. To be specific, the end surfaces 54 of the
ribs 31 and 41 are tilted surfaces open downward. To be more
specific, the end surfaces 54 are tilted surfaces having a
predetermined angle A, in which their lower portions are more
distant from the heat transfer surfaces 20a and 20b than their
upper portions. Because of this, the tip end portion of the rib 31
has a triangular shape in which its upper portion has a tip portion
55 protruding in an acute angle form. The tip end of the tip
portion 55 of the rib 31 and the tip end of the tip portion 55 of
the rib 41 are distant a predetermined dimension D1 from the heat
transfer surfaces 20a and 20b of the plate heater 20, respectively.
Because of this structure, between the rib 31 and the heat transfer
surface 20a of the plate heater 20, a throttle passage 38 which has
an opening width D1 and has a slit shape is formed, while between
the rib 41 and the heat transfer surface 20b of plate heater 20, a
throttle passage 48 which has an opening width D1 and has a slit
shape is formed.
[0111] Like the case where the throttle passages 37 and 47 are
provided, the high-pressure washing water migrates from the
upstream space 25a to the downstream space 25b through the throttle
passages 38 and 48. In the case of the throttle passages 38 and 48,
since the end surfaces 54 of the ribs 31 and 41 are the tilted
surfaces open downward (toward the upstream space 25a), high-speed
flow of the washing water flowing in close proximity to heat
transfer surfaces 20a and 20b of the plate heater 20 can be formed.
This can suppress the washing water from getting stagnant in the
vicinity of heat transfer surfaces 20a and 20b, and hence improve
the heat transfer rate.
[0112] As described above, in the present embodiment, the plate
heater 20 is configured in such a manner that the heat generation
density is lower in the portion closer to the water outlet 23b than
in the portion closer to the water inlet 23a. The passage space 25
has the upstream space 25a including the opening of the water inlet
23a, and the downstream space 25b including the opening of the
water outlet 23b. Between the upstream space 25a and the downstream
space 25b, the throttle passages 37 and 47 having smaller flow
passage cross-sectional areas than another portion are provided.
Because of these, the washing water which has flowed into the heat
exchanger 10A through the water inlet 23a of the casing 23 is
heated while flowing through the passage space 25 defined by the
heat transfer surfaces of the plate heater 20, so that the
temperature of the washing water gradually increases as the washing
water is flowing toward the water outlet 23b.
[0113] In this case, the surface temperature of a portion of the
plate heater 20, which is closer to water inlet 23a, is going to
rise due to the relatively high heat generation density, but a
large amount of heat is taken away from that portion by the washing
water which has not been heated yet and has a low temperature.
Therefore, the surface temperature does not rise up to a high
temperature at which local boiling will take place. In addition,
the washing water flowing from the upstream space 25a toward the
downstream space 25b increases its flow speed by passing through
the throttle passages 37 and 47. Because of this, particularly in
the downstream space 25b, the rate of heat transfer from the plate
heater 20 to the washing water can be improved, a heat transfer
rate distribution can be optimized, and the air bubbles can be
guided quickly to the water outlet 23b. In the portion closer to
the water outlet 23b, since the washing water contacting the
surface of the plate heater 20 has already been heated up to a high
temperature, the amount of heat taken away from that portion by the
washing water is lessened, assuming that the surface temperature of
the plate heater 20 is constant in that portion. However, the plate
heater 20 is configured in such a manner that the heat generation
density is lower in the portion closer to the water outlet 23b than
in the portion closer to the water inlet 23a. Therefore, the
surface temperature does not rise up to a high temperature at which
local boiling will take place.
[0114] As described above, between the upstream space 25a and the
downstream space 25b, the throttle passages 37 and 47 having
smaller flow passage cross-sectional areas than another portion are
provided, and the plate heater 20 is configured in such a manner
that the heat generation density is lower in in the portion closer
to the water outlet 23b than that in the portion closer to the
water inlet 23a. Because of this, the heat transfer rate can be
improved, and the heat transfer rate distribution can be optimized.
In addition, it is possible to suppress the temperature from rising
up to a high temperature at which local boiling will take place, on
the surface of the boundary between the washing water and the
portion of the plate heater 20 which is closer to water outlet 23b,
where the temperature of the washing water tends to be high. As a
result, generation of the air bubbles is suppressed, and the
generated air bubbles are guided quickly to the water outlet 23b.
In this way, it is possible to prevent the scale from being
generated and from adhering to the plate heater 20. As a result, a
heat exchanger which has a longer life can be realized.
Embodiment 2
[0115] FIG. 8 is a view showing another configuration of the heat
exchanger 10. FIG. 8(a) shows the heat exchanger 10 in a state
where the second passage forming member 22 is removed, when viewed
from the base surface 30a side of the first passage forming member
21, and FIG. 6(b) shows an example of a flow of washing water. As
shown in FIG. 8(a), the heat exchanger 10 (10B) has a rib 61
extending horizontally from a region closer to the water inlet 23a.
The rib 61 is bent at a position and then extends vertically
upward.
[0116] To be more specific, one end portion 61a of the rib 61 in
X-direction is located in the vicinity of a region above the
opening of the water inlet 23a at the passage space side, and is in
contact with the inner wall surface of one end portion of the
flange portion 32 in X-direction. The rib 61 extends along
X-direction from one end portion 61a in X-direction on the base
surface 30a, while an opposite end portion 61b thereof in
X-direction is located apart a predetermined distance from the
inner wall surface of an opposite end portion of the flange portion
32 in X-direction. The rib 61 is bent at the opposite end portion
61b and extends upward, and an upper end portion 61c of the rib 61
is in contact with the inner wall surface of an upper portion of
the flange portion 32. The rib 61 separates the passage space 25
into the upstream space 25a having a substantially-L shape and the
downstream space 25b of a rectangular shape.
[0117] The upstream space 25a includes a space (horizontal space)
62 defined by a portion between the end portions 61a and 61b of the
rib 61 and extending horizontally, and a space (vertical space) 63
defined by a portion between the end portions 61b and 61c of the
rib 61 and extending vertically, thereby forming the above
substantially-L shape. The second passage forming member 22 has a
rib symmetric with the rib 61.
[0118] Because of the presence of the rib 61, there is provided a
throttle passage (horizontal throttle passage and vertical throttle
passage) 65 having a smaller flow passage cross-sectional area than
the upstream space 25a and the downstream space 25b. By combining
the passage forming member 21, the passage forming member 22, and
the plate heater 20, a slit-shape horizontal throttle passage 65a
is provided between the portion between the end portions 61a and
61b of the rib 61 and the first heat transfer surface 20a of the
plate heater 20, and a slit-shape vertical throttle passage 65b is
provided between the portion between the end portions 61b and 61c
of the rib 61 and the first heat transfer surface 20a of the plate
heater 20.
[0119] In the present embodiment, the rib 61 has a constant height
from the base surface 30a over the entire length from the end
portion 61a to the end portion 61c, and the base surface 30a and
the first heat transfer surface 20a are placed in parallel.
Therefore, the horizontal throttle passage 65a and the vertical
throttle passage 65b have substantially the same opening width.
[0120] As shown in FIG. 8(b), in the heat exchanger 10B including
the throttle passage 65 configured as described above, high-speed
water flows from the horizontal space 62 to the downstream space
25b through the horizontal throttle passage 65a, and flows
vertically upward as described in Embodiment 1. In the heat
exchanger 10B of the present embodiment, in addition, the
high-speed water flows from the vertical space 63 into the
downstream space 25b through the vertical throttle passage 65b, and
then flows horizontally. Therefore, in the downstream space 25b,
vertically upward water flow and horizontal water flow are mixed,
and thereby disordered water flow is generated. The disordered
water flow causes the washing water to be agitated. As a result,
the heat transfer rate can be improved. Like Embodiment 1, the
plate heater 20 is configured in such a manner that the heat
generation density is lower in the portion closer to the water
outlet 23b than in the portion closer to the water inlet 23a, and
the air bubbles can be discharged quickly to outside through the
water outlet 23b.
Embodiment 3
[0121] FIG. 9 is a view showing another configuration of the heat
exchanger 10. FIG. 9(a) shows the heat exchanger 10 in a state
where the second passage forming member 22 is removed, when viewed
from the base surface 30a side of the first passage forming member
21, and FIG. 9(b) shows an example of a flow of washing water. As
shown in FIG. 9(a), the heat exchanger 10(10C) includes the
straight and horizontal rib 31 similar to that described in
Embodiment 1. In addition, inside the downstream space 25, a
plurality of agitating walls 67 which are corrugated in shape are
provided.
[0122] To be more specific, the rib 31 protrudes from the base
surface 30a of the first passage forming member 21 so as to extend
horizontally from the inner wall surface of one end side of the
flange portion 32 in X-direction to the inner wall surface of an
opposite end side of the flange portion 32 in X-direction.
Therefore, the rib 31 forms the throttle passage 37 similar to that
of Embodiment 1. The agitating walls 67 extend from the rib 31
upward along the base surface 30a. The agitating walls 67 extend
upward such that they are curved in a circular-arc shape like a
sine waveform having a specified amplitude in X-direction. The
plurality (six in the present embodiment) of agitating walls 67 are
arranged at substantially equal intervals in X-direction.
[0123] The height of the agitating walls 67 from the base surface
30a is substantially equal to or a little smaller than the height
of the rib 31. Adjacent two agitating walls 67 are spaced apart
from each other so as not to overlap with each other when viewed
from above along Z-direction. In other words, between the adjacent
two agitating walls 67, there is a route through which the washing
water can migrate straightly from the lower side to the upper side
without migrating horizontally to avert the agitating walls 67.
[0124] In accordance with the heat exchanger 10C, as shown in FIG.
9(b), the water which has flowed from the throttle passage 37 at a
high speed into the downstream space 25b collides against the
agitating walls 67 and is agitated. This results in an improved
heat transfer rate. Even though the washing water is agitated by
the agitating walls 67, the air bubbles are allowed to migrate
quickly toward the water outlet 23b. That is, since the route
through which the washing water migrates straightly in the upward
and downward direction is formed between the adjacent two agitating
walls 67 as described above, the air bubbles which are going to
migrate upward by a buoyancy force or the like, are less likely to
be impeded by the agitating walls 67, and therefore can migrate
upward quickly.
Embodiment 4
[0125] FIG. 10 shows another configuration of the heat exchanger
10. FIG. 10(a) shows the heat exchanger 10 in a state where the
second passage forming member 22 is removed, when viewed from the
base surface 30a side of the first passage forming member 21, and
FIG. 10(b) shows an example of a flow of washing water. As shown in
FIG. 10(a), the heat exchanger 10(10D) includes the rib 61 of a
substantially-L shape similar to that of Embodiment 2, while inside
the downstream space 25, the agitating walls 67 similar to those of
Embodiment 3 are provided.
[0126] In accordance with the heat exchanger 10D, as shown in FIG.
10(b), the water flow migrating vertically upward from the throttle
passage 65a and the water flow migrating horizontally from the
throttle passage 65b cause a disordered flow to be generated in the
downstream space 25b. The disordered flow agitates the water flow.
In addition, the agitating walls 67 also agitate the water flow.
Therefore, the heat transfer rate can be further improved. The air
bubbles are less likely to be impeded by the agitating walls 67.
Therefore, the air bubbles can migrate upward quickly and can be
discharged to outside from the water outlet 23b.
Embodiment 5
[0127] FIG. 11 is a view showing another configuration of the heat
exchanger 10. FIG. 11(a) shows heat exchanger 10 in a state where
the second passage forming member 22 is removed, when viewed from
the base surface 30a side of the first passage forming member 21.
FIG. 11(b) is a cross-sectional view of the heat exchanger 10 taken
along B-B. FIG. 11(c) is a cross-sectional view of the heat
exchanger 10 taken along C-C. As shown in FIGS. 11(a), the heat
exchanger 10(10E) of the present embodiment has the same
configuration in a larger part as that of Embodiment 1, but
includes a rib 71 which is a little different from the rib 31 of
Embodiment 1. Therefore, the rib 71 will now be described in
detail.
[0128] As shown in FIG. 11(a), like the rib 31 of Embodiment 1, one
end portion 71a of the rib 71 in X-direction is located in the
vicinity of a region above an opening of the water inlet 23a at the
passage space side, and is in contact with the inner wall surface
of one end portion of the flange portion 32 in X-direction. The rib
71 extends along X-direction from one end portion 71a in
X-direction on the base surface 30a, and an opposite end portion 7
lb thereof in X-direction is in contact with the inner wall surface
of an opposite end portion of the flange portion 32 in
X-direction.
[0129] The rib 71 is provided with a plurality of remaining
portions 72 formed (left) by cutting portions of the rib 71 at a
tip end portion thereof. These remaining portions 72 are, as shown
in FIG. 11(a), arranged at substantially equal intervals along the
longitudinal direction of the rib 71. As shown in FIG. 11(c), an
end surface 74 of the tip end portion (end portion of the rib 71 in
Y-direction which is closer to the heat transfer surface 20a of the
plate heater 20) of the rib 71 is a tilted surface open downward
and the tip end portion of the rib 71 has a triangular shape in
which the upper portion of the tip end portion has a tip portion 75
protruding in an acute angle form like the structure shown in FIG.
7(b). The remaining portions 72 having a predetermined depth are
formed on the tip portion 75.
[0130] As a result of the above, as shown in FIG. 11(b), between
the rib 71 and the first heat transfer surface 20a (indicated by
two-dotted line) of the plate heater 20, a slit-shape throttle
passage 78 having an opening width D1 is formed. In addition,
because of the presence of the remaining portions 72,
increased-width portions 78a having an opening width D2 greater
than the dimension D1 of a portion other than the increased-width
portions 78a. Although not shown, the second passage forming member
22 is provided with the rib 71 having the above structure and being
symmetric with the rib 71. The throttle passage 78 having the above
structure is formed between the rib 71 and the second heat transfer
surface 20b of the plate heater 20.
[0131] In accordance with the heat exchanger 10E of the present
embodiment, the opening width of the throttle passage 78 is not
constant, but the throttle passage 78 has portions of the dimension
D1 and portions defined by the increased-width portions 78a of the
dimension D2 (>D1). Because of this structure, when the washing
water is flowing from the upstream space 25a to the downstream
space 25b through the throttle passage 78, there is a speed
difference between the water flowing through the increased-width
portions 78a and the water flowing through the portions other than
the increased-width portions 78a. As a result, the washing water is
agitated by a plurality of water flows with different speeds in the
downstream space 25b, thereby improving the heat transfer rate.
[0132] Although the rib 71 has the tip portion 75 at the upper
portion of the tip end portion thereof like the rib 31 of FIG.
7(b), the present invention is not limited to this. For example,
the remaining portions may be formed at the tip portions of the
lower portion of the tip end portion, as shown in FIG. 7(a).
Embodiment 6
[0133] FIG. 12 is a view showing another configuration of the heat
exchanger 10. FIG. 12(a) shows heat exchanger 10 in a state where
the second passage forming member 22 is removed, when viewed from
the base surface 30a side of the first passage forming member 21.
FIG. 12(b) is a cross-sectional view of the heat exchanger 10 taken
along B-B.
[0134] As shown in FIG. 12(a), the heat exchanger 10(10F) has a
configuration similar to that of the heat exchanger 10E having the
rib 71 described in Embodiment 5 (FIG. 11). In addition, each of
the first passage forming member 21 and the second passage forming
member 22 of the heat exchanger 10F is provided with a plurality of
buffer walls 81 arranged in the upward and downward direction (in
Z-direction) so as to extend horizontally (in X-direction) in a
region corresponding to the downstream space 25b.
[0135] The buffer walls 81 of the first passage forming member 21
protrude from the base surface 30a with a dimension substantially
equal to that of the rib 71, and extends from one end portion of
the flange portion 32 in X-direction to an opposite end portion of
the flange portion 32 in X-direction like the rib 71. As shown in
FIG. 12(b), the downstream space 25b is separated into a plurality
of buffer spaces 82 (in the present embodiment, three buffer spaces
82a.about.82c) by the buffer walls 81 such that the buffer spaces
82a.about.82c are arranged in the upward and downward direction.
The adjacent upper and lower buffer spaces 82 communicate with each
other only through the slit-shape throttle passage 83 formed
between the buffer wall 81 and the first transfer surface 20a of
the plate heater 20. The second passage forming member 22 is
provided with the buffer walls 81 having the same structure.
[0136] The buffer walls 81 have a smaller height than the rib
71.
[0137] In accordance with the heat exchanger 10F, the washing water
flows into the lowermost buffer space 82a of the downstream space
25b through the throttle passage 78 formed by the rib 71, where the
water flow is disordered and agitated. Since the buffer wall 81 is
located relatively closer to the rib 71, the water flow with a
relatively high speed which has passed through the throttle passage
78 collide with the buffer wall 81, thereby promoting generation of
a disturbed flow in the buffer space 82a.
[0138] Then, the washing water flows from the buffer space 82a into
the buffer space 82b located above and adjacent to the buffer space
82a, while increasing its speed by passing through the narrower
throttle passage 83. Since the water flow contacts the first heat
transfer surface 20a of the plate heater 20 at a higher speed, the
rate of heat transfer from the first heat transfer surface 20a to
the washing water can be improved. Furthermore, since generation of
a disordered flow in the buffer space 82b is promoted by the fact
that the high-speed water flow collides against the buffer wall 81
located next, the heat transfer rate can also be improved.
Thereafter, in the same manner, similar phenomenon occurs and the
heat transfer rate can be improved in the buffer space 82c.
[0139] Since the buffer walls 81 have a smaller height than the rib
71 as described above, the generated air bubbles can be discharged
in an upward direction.
Embodiment 7
[0140] FIG. 13 is a view showing another configuration of the heat
exchanger 10. FIG. 13(a) shows the heat exchanger 10 in a state
where the second passage forming member 22 is removed, when viewed
from the base surface 30a side of the first passage forming member
21. FIG. 13(b) is a cross-sectional view of the heat exchanger 10
taken along B-B. As shown in FIG. 13(a), the heat exchanger 10
(10G) has a configuration similar to that of the heat exchanger 10
(10F) described in Embodiment 6 (FIG. 12), and is configured in
such a manner that the buffer walls 81 is provided with remaining
portions 88 formed by cutting portions of the buffer walls 81 at
suitable locations.
[0141] To be more specific, as shown in FIG. 13(a), the heat
exchanger 10G according to the present embodiment includes three
buffer walls 81 (81a.about.81c) arranged in the upward and downward
direction. The buffer walls 81a.about.81c are provided with
remaining portions 88 formed (left) by cutting portions of the
buffer walls 81a.about.81c such that the remaining portions 88 are
different in position between adjacent upper and lower buffer walls
81a and 81b when viewed from above (when viewed in Z-direction),
and between adjacent upper and lower buffer walls 81b and 81c when
viewed from above.
[0142] To be specific, the lowermost buffer wall 81a is provided
with one remaining portion 88 in the vicinity of a center portion
in the longitudinal direction thereof (X-direction). The buffer
wall 81b located above the buffer wall 81a is provided with
remaining portions 88 at two positions which are in the vicinity of
one end portion thereof in the longitudinal direction and in the
vicinity of an opposite end portion thereof in the longitudinal
direction. The buffer wall 81c located above the buffer wall 81b is
provided with one remaining portion 88 in the vicinity of a center
portion in the longitudinal direction, like the buffer wall 81a.
The above illustrated number and positions of the remaining
portions 88 are exemplary, but the remaining portions 88 may be
provided at positions different from those as described above so
long as they do not overlap with each other between the adjacent
upper and lower buffer walls 81 as viewed above. In addition, the
cut portion depth and cut portion length of the remaining portions
88 are not particularly limited.
[0143] In accordance with the heat exchanger 10G as described
above, in the buffer spaces 82a.about.82c, there are generated a
flow of the washing water which is migrating upward through the
narrower portions of the throttle passage 78 which are not provided
with the remaining portions 88 and a flow of the washing water
which is migrating horizontally toward the remaining portions 88 to
flow through the increased-width portions defined by the remaining
portions 88. Since the vertically upward water flow and the
horizontal water flow are mixed, generation of a disordered flow in
the downstream space 25b is promoted. As a result, the rate of heat
transfer from the plate heater 20 to the washing water can be
improved.
[0144] To quickly guide the air bubbles generated in the passage
space 25 toward the water outlet 23b, a ceiling surface defining
the downstream space 25b may be a tilted surface. FIG. 14 is a view
showing a modified example of the heat exchanger 10A of Embodiment
1, and showing the heat exchanger 10A in a state where the second
passage forming member 22 and the plate heater 20 are removed, when
viewed from the base surface 30a side of the first passage forming
member 21.
[0145] As shown in FIG. 14, the ceiling surface (in this modified
example, inner upper surface of the first passage forming member
21) defining the downstream space 25b is formed as a tiled surface
which is lower as it is away from the region in the vicinity of the
water outlet 23b. In such a configuration, the air bubbles
migrating upward due to the flow of the washing water or a buoyancy
force in the downstream space 25b are guided smoothly toward the
water outlet 23b along the tilted ceiling surface 21a. This makes
it possible to discharge the air bubbles in the downstream space
25b quickly through the water outlet 23b. The tilted ceiling
surface 21s may be applied to heat exchangers 10H.about.10J
described below and the above described heat exchangers
10B.about.10G, as well as the heat exchanger 10A of Embodiment
1.
[0146] [Configuration in Which a Bypass Passage is Provided]
[0147] Next, a description will be given of heat exchangers of
Embodiments 8.about.11, each of which includes, in a passage space,
a sinuous passage extending from the water inlet to the water
outlet, the sinuous passage having a passage for guiding the
washing water in one direction in a horizontal direction and a
passage for guiding the washing water in an opposite direction in
the horizontal direction such that they are arranged alternately
from the lower side to the upper side, and bypass passages each of
which is provided in the upward and downward direction and allows
adjacent upper and lower passages in the sinuous passage to
communicate with each other. Note that any one of the heat
exchangers 10 of these embodiments may be incorporated into the
sanitary washing device 1 of FIG. 1 as the heat exchanger 10. A
plate heater 120 included in each heat exchanger 10 described below
has a configuration similar to that of the plate heater 20
(especially configuration of the pattern 20p of the resistive
element) described with reference to FIGS. 4 and 5.
Embodiment 8
[0148] [Heat Exchanger]
[0149] FIG. 15 is a view showing a configuration of a heat
exchanger 10(10H). FIG. 15(a) is a front view showing a
configuration of an external appearance of the heat exchanger 10.
FIG. 15(b) is a cross-sectional view of the heat exchanger 10 taken
along B-B. As shown in FIGS. 15(a) and 15(b), in its external
appearance, the heat exchanger 10H has a small thickness and a
rectangular plate shape when viewed from the front. As shown in
FIG. 15(b), the heat exchanger 10H includes a rectangular plate
heater 120, a first passage forming member 121 disposed to face one
surface (first heat transfer surface) 120a, a second passage
forming member 122 disposed to face an opposite surface (second
heat transfer surface) 120b, and a casing 123 accommodating, the
plate heater 120, the first passage forming member 121 and the
second passage forming member 122, and having a water inlet 123a
and a water outlet 123b. The plate heater 120 is made of ceramic,
while the first passage forming member 121 and the second passage
forming member 122, are made of reinforced ABS resin formed by
compounding glass fiber into ABS resin.
[0150] Hereinafter, a description will be given of a state where
the heat exchanger 10H is placed to be oriented vertically such
that the heat transfer surfaces of the plate heater 120 are
parallel to the vertical direction, except for cases specially
noted. As shown in FIG. 15, the vertical direction is Z-direction,
a direction perpendicular to Z-direction and parallel to the heat
transfer surfaces of the plate heater 20 is X-direction, and a
direction (direction perpendicular to the first heat transfer
surface 120a) perpendicular to X-direction and Z-direction is
Y-direction.
[0151] As shown in FIG. 15(b), the first passage forming member 121
includes a base portion 130 of a rectangular plate shape which
faces the first heat transfer surface 120a, and a plurality of wall
portions (ribs) 131 protruding from a surface (base surface) 130a
of the base portion 130 which faces the first heat transfer surface
120a. Likewise, the second passage forming member 122 includes a
base portion 140 of a rectangular plate shape which faces the
second heat transfer surface 120b, and a plurality of wall portions
(ribs) 141 protruding from a surface (base surface) 140a of the
base portion 140 which faces the second heat transfer surface
120b.
[0152] A wall-like flange portion 132 is provided to extend along
the peripheral edge portion of the base portion 130 of the first
passage forming member 121. The flange portion 132 extends a
predetermined dimension toward the second passage forming member
122. An engagement groove 133 is formed at the tip end portion of
the flange portion 132 so as to extend along the flange portion
132. A wall-like flange portion 142 is provided to extend along the
peripheral edge portion of the base portion 140 of the second
passage forming member 122. The flange portion 142 is extended by a
predetermined dimension in a direction away from the first passage
forming member 121. The tip end portion of the flange portion 142
is turned back toward the first passage forming member 121. An
engagement projection 143 is formed at the end portion of the
flange portion 142 so as to extend along the flange portion
142.
[0153] The first passage forming member 121 is externally fitted to
the second passage forming member 122 such that the base surface
130a faces the base surface 140a. To be more specific, the flange
portion 132 of the first passage forming member 121 is externally
fitted to the flange portion 142 of the second passage forming
member 122, and the engagement projection 143 of the second passage
forming member 122 is fitted into the engagement groove 133 of the
first passage forming member 121 (e.g., the engagement projection
143 is secured to the engagement groove 133 by ultrasonic
fusion-bonding.) This allows the first passage forming member 121
and the second passage forming member 122 to be joined in a sealed
state, thereby forming a passage space 125.
[0154] As shown in FIG. 5(a), the water inlet 123a is provided at
the lower portion of one end portion of the casing 123 in
X-direction, while the water outlet 123b is provided at the upper
portion of one end portion of the casing 123 in X-direction. As
shown in FIG. 15(b), the water inlet 123a and the water outlet 123b
communicate with the passage space 125.
[0155] FIG. 16 is an exploded view of the heat exchanger 10H. FIG.
16(a) shows the heat exchanger 10H in a state where the second
passage forming member 122 and the plate heater 120 are removed,
when viewed from the base surface 130a side of the first passage
forming member 121, and FIG. 16(b) shows the second passage forming
member 122 when viewed from the base surface 140a side thereof. As
shown in FIG. 16(a), a plurality of (in the present embodiment,
seven) wall portions (ribs) 131 (131a.about.131g) are arranged in
the upward and downward direction (in Z-direction) extending
substantially horizontally (in X-direction) on the base surface
130a of the base portion 130 of the first passage forming member
121.
[0156] Among the wall portions (ribs) 131a.about.131g, the wall
portions (ribs) 131a, 131c, and 131e which are in odd-numbered
orders from the bottom are each configured in such a manner that
one end portion (one end portion in X-direction) in the
longitudinal direction thereof is in contact with the inner wall
surface of the flange portion 132 and an opposite end portion in
the longitudinal direction is apart a predetermined dimension from
the inner wall surface of the flange portion 132. The wall portions
131b, 131d, and 131f which are in even-numbered orders from the
bottom are each configured in such a manner that one end portion in
the longitudinal direction (one end portion in X-direction) is
apart from the inner wall surface of the flange portion 132 and an
opposite end portion thereof in the longitudinal direction is in
contact with the inner wall surface of the flange portion 132. In
the passage space 125, a sinuous passage 135 is defined by the wall
portions (ribs) 131a.about.131g.
[0157] To be more specific, a passage 135a defined by the lower
portion of the flange portion 132 as its lower side and the
lowermost wall portion (rib) 131a as its upper side serves to guide
the washing water in a direction from one side in X-direction where
the water inlet 123a is located, toward an opposite side in
X-direction. The washing water reaches the downstream end of the
passage 135a and then its flow is turned back at the downstream
end. The washing water is guided from the opposite side in
X-direction to one side in X-direction through a passage 135b
defined by the wall portion (rib) 131a as its lower side and the
wall portion (rib) 131b as its upper side, which is located above
the wall portion 131a. After that, in the same manner, the washing
water is turned back and guided in the opposite direction, along
the passages 135c.about.135h, and finally to the water outlet 123b.
The sinuous passage 135 is constituted by the passages
135a.about.135h (see FIG. 19 as described later).
[0158] As shown in FIG. 16(b), the wall portions (ribs) 141 of the
second passage forming member 122 have the same structure as
aforesaid wall portions (ribs) 131 of the first passage forming
member 121, except that the wall portions (ribs) 141 are symmetric
with the wall portions (ribs) 131, and they will not be described
in detail. In a similar manner, the wall portions 141 form a
sinuous passage 145 extending from the water inlet 123a to the
water outlet 123b. The plate heater 120 having a substantially
constant width and a rectangular shape is sandwiched between the
first passage forming member 121 and the second passage forming
member 122 (see the plate heater 20 in FIGS. 4 and 5).
[0159] FIG. 17 is a cross-sectional view of the heat exchanger 10
taken along XVII-XVII of FIG. 16(a). As shown in FIG. 17, the wall
portion (rib) 131 has a structure in which a longitudinal dimension
(dimension in X-direction) is L1, and a height H1 from the base
surface 130a along the longitudinal direction is substantially
constant. Note that a remaining portion 136 having an opening
dimension (dimension in X-direction) L2 and a depth H2 is formed at
a portion (in the present embodiment, center portion) in the
longitudinal direction.
[0160] FIG. 18 is a view showing a structure of the wall portion
(rib portion) 131 and the remaining portion 136. FIG. 18(a) is an
enlarged view of a portion XVIIIa in FIG. 17, to show the remaining
portion 136 taken along Z-direction. FIG. 18(b) is an enlarged view
of a portion XVIIIb in FIG. 15, to show the remaining portion 136
taken along X-direction. As shown in FIG. 18(a), the remaining
portion 136 has a shape in which the tip end portion of the wall
portion (rib) 131 is cut in a rectangular shape, and is dented with
respect to another portion of the wall portion (rib) 131. A deepest
portion 136a of the remaining portion 136 is substantially parallel
to the upper end of the wall portion (rib) 131. In the heat
exchanger 10H of the present embodiment, an opening dimension L2 of
the remaining portion 136 is set to satisfy the following formula
(1) with respect to the length L1 of the wall portion (rib)
131:
1/2.gtoreq.(L2/L1).gtoreq.1/5 (1).
For example, L2=20 mm.
[0161] As shown in the cross-sectional view of FIG. 18(b), the tip
end surface of the wall portion (rib) 131 is not parallel to the
surface (first heat transfer surface 120a) of the plate heater 120,
but is a tilted surface having a predetermined angle A. The tip end
portion of the wall portion (rib) 131 has a triangular shape in
which its lower portion forms a tip portion 137 having an acute
angle shape in cross-section. The remaining portion 136 is formed
in the tip portion 137. The remaining portion 136 constitutes the
bypass passage 138 which allows communication between a lower
passage defined by the wall portion (rib) 131 and an upper passage
defined by the wall portion (rib) 131.
[0162] As shown in FIG. 18(b), in a state where the first passage
forming member 121 and the second passage forming member 122 are
disposed to sandwich the plate heater 120, a portion of the tip end
portion other than the remaining portion 136 in the wall portion
(rib) 131 is a dimension H3 apart from the first heat transfer
surface 120a of the plate heater 120. In the heat exchanger 10H of
the present embodiment, the dimension H3 is set to satisfy the
following formula (2), with respect to a dimension H4 from the base
surface 130a of the first passage forming member 121 to the first
heat transfer surface 120a:
1/4.gtoreq.(H3/H4).gtoreq. 1/10 (2).
For example, H3=0.2 mm, and H4=1.9 mm.
[0163] The wall portion (rib) 141 of the second passage forming
member 122 has the same cross-sectional shape as that of the wall
portion (rib) 131 and is set to satisfy the formula (2). And, the
wall portion (rib) 141 is provided with a remaining portion 146
having a depth H2 (see FIG. 18(b)). The remaining portion 146 forms
a bypass passage 148 which allows communication between adjacent
upper and lower passages sandwiching the wall portion (rib)
131.
[0164] By setting (L2/L1) to (1/2) or less in the formula (1), it
is possible to more easily and sufficiently ensure water (water
amount) flowing from upstream to downstream through the sinuous
passage 135 (or sinuous passage 145) than water (water amount)
flowing from upstream to downstream through the bypass passage 138
(or bypass passage 148). This allows the heat exchanger 10H to
perform its original heat exchange function well.
[0165] By setting (L2/L1) to (1/5) or more in the formula (1), the
flow passage cross-sectional area of the bypass passage 138 (or
bypass passage 148) is more sufficiently ensured relative to the
sinuous passage 135 (or sinuous passage 145). This allows the air
bubbles to be guided to the water outlet 123b and discharged to
outside more easily and surely through the bypass passage 138 (or
bypass passage 148).
[0166] By setting (H3/H4) to (1/4) or less in the formula (2)
described above, it is possible to more easily and sufficiently
ensure water (water amount) flowing from upstream to downstream
through the passage 135a located at mostupstream side of the
sinuous passage 135 (or a passage which is located at mostupstream
side of the sinuous passage 145 and is plane-symmetric with respect
to the passage 135a, and hereinafter this passage is referred to as
"passage 145a"), rather than water (water amount) flowing out into
a space between the wall portion (rib) 131 (or 141) and the first
heat transfer surface 120a (or second heat transfer surface 120b).
Since water (water amount) flowing from upstream to downstream
through the passage 135a located at mostupstream side of the
sinuous passage 135 (or the passage 145a located at mostupstream
side of the sinuous passage 145) can be ensured more easily and
sufficiently, water (water amount) flowing from upstream to
downstream through the sinuous passage 135 (or sinuous passage 145)
can be ensured more easily and efficiently. This allows the heat
exchanger 10H to perform its original heat exchange function
better.
[0167] By setting (H3/H4) to ( 1/10) or more in the formula (2), a
wider space is provided between the wall portion (rib) 131 (or 141)
and the first heat transfer surface 120a (or second heat transfer
surface 120b). This makes it possible to easily and surely prevent
thermal effect (thermal dissolution, thermal deformation, etc.,)
from the first heat transfer surface 120a (or second heat transfer
surface 120b) to the wall portion (rib) 131 (or 141).
[0168] As shown in FIG. 18(b), the lower end portion of the plate
heater 120 is apart from the lower inner wall surface of the flange
portion 132 of the first passage forming member 121. Therefore, a
space below the lower end portion of the plate heater 120 is a
common space (upstream common space) 125a for the sinuous passage
135 at the first heat transfer surface 120a side of the plate
heater 120 and the sinuous passage 145 side of the second heat
transfer surface 120b side of the plate heater 120. The washing
water which has flowed into the passage space 125 through the water
inlet 123a is divided to flow to the sinuous passages 135 and 145
through the upstream common space 125a. Likewise, as shown in FIG.
15(b), the upper end portion of the plate heater 120 is apart from
the upper inner wall surface of the flange portion 132 of the first
passage forming member 121. A space above the upper end portion of
the plate heater 120 is a common space (downstream common space)
125b for the sinuous passages 135 and 145. Therefore, the washing
water flowing through the sinuous passage 135 and the washing water
flowing through the sinuous passage 145 are joined together in the
downstream common space 125b, and the resulting washing water flows
toward the water outlet 123b.
[0169] FIG. 19 is a view showing the flow of the washing water and
the flow of the air bubbles in the heat exchanger 10H configured as
described above. Like the configuration shown in FIG. 16(a), the
flow of the washing water and the flow of the air bubbles are
viewed from the perspective of the base surface 130a side of the
first passage forming member 121. As shown in FIG. 19, a most part
of the washing water with a low temperature (e.g., 5 degrees C.)
which has flowed into the heat exchanger 10H through the water
inlet 123a flows upward along the sinuous passage 135 (and sinuous
passage 145) such that its flow direction is inverted from one
direction in X-direction to an opposite direction in X-direction or
from the opposite direction to the one direction in the order of
the passages 135a.about.135h (see solid-line arrows in FIG. 19).
When the washing water is flowing through the passages 135a to
135h, the temperature of the washing water is raised up to a
suitable temperature (e.g., 40 degrees C.) by heat transfer from
the plate heater 120, and then is discharged to outside through the
water outlet 123b. The washing water, the temperature of which has
been raised in this way, is ejected in a shower form to the private
part of the human body through the nozzle of the washing unit as
described above.
[0170] Hereinafter, a description will be given of the operation
and action of the heat exchanger configured as described above. The
washing water flowing into the heat exchanger 10H through the water
inlet 123a of the casing 123 is heated while flowing through the
passage 135 defined by the heat transfer surface of the plate
heater 120. The temperature of the washing water gradually
increases as it is getting closer to the water outlet 123b. The
surface temperature of the portion of the plate heater 120 which is
closer to water inlet 123a is going to rise due to a relatively
high heat generation density. But, a large amount of heat is taken
away from that portion by the washing water which has not been
heated yet. Therefore, the surface temperature of the plate heater
120 does not rise up to a high temperature at which local boiling
will take place.
[0171] In a portion of the heat exchanger 10H which is closer to
water outlet 123b, the washing water is in a higher-temperature
condition than the washing water in a portion of the heat exchanger
10H which is closer to the water inlet 123a. Therefore, heat taken
away by the washing water from the surface of the plate heater 120
corresponding to this portion is lessened. But, the plate heater
120 is configured in such a manner that the heat generation density
is lower in the portion closer to the water outlet 123b than in the
portion closer to water inlet 123a, and the temperature of that
portion does not rise up to a high temperature at which local
boiling will take place.
[0172] Since the plate heater 120 is configured in such a manner
that the heat generation density is lower in the portion closer to
the water outlet 123b than in the portion closer to water inlet
123a, its temperature is suppressed from rising up to a high
temperature at which local boiling will take place, on the surface
of the boundary between the plate heater 120 and the water in the
portion of the plate heater 120 which is closer to water outlet
123b where the temperature of the washing water tends to be higher.
As a result, formation and adhesion of the scale can be prevented,
and a heat exchanger having a longer life can be realized.
[0173] In accordance with the heat exchanger 10H of the present
embodiment, heat exchange is performed in such a manner that heat
of the plate heater 120 is transferred to the washing water flowing
while contacting the obverse and reverse heat transfer surfaces of
the plate heater 120, and a heat efficiency is high without a
substantial heat release loss. Therefore, the heat exchanger 10H
can be small-sized. In addition, the sinuous passage 135 and the
sinuous passage 145 can increase the passage length and increase
the flow speed. Therefore, in the washing water flowing through the
sinuous passage 135 and 145, a boundary layer to which heat is
substantially transferred from the surface of the plate heater 120
is thinned. Because of this, the heat transfer rate can be
improved, and the temperature of the surface of the heater is
suppressed from rising. As a result, local boiling can be
suppressed, and formation and adhesion of the scale can be
prevented more effectively.
[0174] As described above, the plate heater 120 of the present
embodiment is configured in such a manner that the heat generation
density is lower in the portion closer to the water outlet 123b
than in the portion closer to the water inlet 123a. In such a
configuration, the heat exchanger 10H of the present invention can
achieve the same advantages as those described in Embodiment 1.
[0175] In the heat exchanger 10H of the present embodiment, the
sinuous passage 135 (or sinuous passage 145) is defined by the
plurality of wall portions 131 arranged vertically to extend
substantially horizontally. The sinuous passage 135 (or sinuous
passage 145) is configured in such a manner that the passage 135a
for guiding the washing water in one direction in the substantially
horizontal direction and the passage 135b for guiding the washing
water in the opposite direction in the substantially horizontal
direction are arranged alternately from the lower side to the upper
side, in a range from the water inlet 123a to the water outlet
123b. Furthermore, in an intermediate portion of each wall portion
131 in the longitudinal direction, the bypass passage 138 (or
bypass passage 148) is provided in the upward and downward
direction to allow communication between adjacent upper and lower
passages 135. This allows the washing water to flow at a high
speed, which can improve the heat transfer rate. In addition, the
air bubbles can be guided quickly to the water outlet 123b through
the bypass passages 138 (or bypass passages 148) provided in the
upward and downward direction at the sinuous passages 135 (or
sinuous passages 145).
[0176] Since the heat exchanger 10H is provided with the sinuous
passages 135 to have smaller flow passage cross-sectional areas,
the flow speed of the washing water can be made high and uniform.
Since the plate heater 120 is configured in such a manner that the
heat generation density is lower in the portion closer to the water
outlet 123b than in the portion closer to the water inlet 123a, the
temperature is suppressed from rising up to a high-temperature at
which local boiling will take place, and the generation of the air
bubbles is suppressed. Even if the air bubbles are generated, the
generated air bubbles can migrate quickly to the water outlet 123b
through the bypass passages 138 (or bypass passages 148) with a
passage length shorter than the overall passage length of the
sinuous passage 135, the bypass passages 138, 148 being provided in
the upward and downward direction on the sinuous passage 135, 145
having a long passage length for guiding the washing water from the
water inlet 123a to the water outlet 123b, to allow the air bubbles
to take a short cut.
[0177] As a result, a passage resistance at one of the heat
transfer surface sides (120a or 120b) of the plate heater 120 can
be prevented from becoming much higher than that at the other heat
transfer surface side (120a or 120b), or only the temperature at
the heat transfer surface (120a or 120b) of the plate heater 120
from increasing significantly, which would be caused by the air
bubbles. Thus, the local boiling which would lead to formation and
adhesion of the scale can be further suppressed. Since the air
bubbles generated on the surface of the plate heater 120 are guided
quickly to the water outlet 123b through the bypass passages 138
(or the bypass passages 148), the air bubbles can be suppressed
from growing to a great size. As a result, a problem that the
operation of a thermistor provided in the vicinity of the water
outlet 123b is impeded by the air bubbles of a great size, will not
arise.
[0178] In the heat exchanger 10H of the present embodiment, the
sinuous passage 135 at the heat transfer surface 120a side of the
plate heater 120 and the sinuous passage 136 at the heat transfer
surface 120b side of the plate heater 120 are symmetric, and the
bypass passage 138 at the heat transfer surface 120a side of the
plate heater 120 and the bypass passage 148 at the heat transfer
surface 120b side of the plate heater 120 are symmetric. This
allows a balance of a heat transfer amount between the obverse and
reverse heat transfer surfaces of the plate heater 120 to be
suitably be maintained As a result, deformation of the plate heater
120 due to a thermal stress can be prevented.
[0179] In the heat exchanger 10H of the present embodiment, the
bypass passages 138 provided on the plurality of wall portions 131
arranged in the upward and downward direction substantially conform
in position to each other when viewed from above. In the same
manner, the bypass passages 148 provided on the plurality of wall
portions 141 arranged in the upward and downward direction
substantially conform in position to each other when viewed from
above. This allows the air bubbles to migrate straightly upward
through the bypass passages 138 and 148 and reach the water outlet
quickly.
[0180] Since the washing water is heated by the plate heater 120,
gaseous component dissolved into the washing water may vaporize to
generate air bubbles, in some cases. The flow (see while arrows in
FIG. 19) of the air bubbles will be discussed. For example, the air
bubbles generated in the passage 135a of the sinuous passage 135
flows through the passage 135a along with the washing water.
However, a buoyancy force acts on the air bubbles and causes them
to migrate upward. Therefore, before reaching the downstream end of
the passage 135a, the air bubbles take a short cut to its upper
adjacent passage 135b through the bypass passage 138 defined by the
remaining portion 136 formed on the wall portion (rib) 131a. Then,
the air bubbles migrate to the uppermost passage 135h through the
bypass passages 138 defined by the remaining portions 136 of the
wall portions (ribs) 131b.about.131g, respectively. Then, the air
bubbles migrate along with the washing water in the passage 135h,
and are discharged to outside through the water outlet 123b. In the
same manner, the air bubbles generated in the passages
135b.about.135g other than the passage 135a migrate to the
corresponding upper passages through the bypass passages 138. In
the same manner, the air bubbles generated in the sinuous passage
145 take a short cut and migrate upward through the bypass passages
148.
[0181] In accordance with the heat exchanger 10H as described
above, the air bubbles generated inside the heat exchanger 10H can
be guided quickly to the water outlet 123b and discharged to
outside.
Embodiment 9
[0182] FIG. 20 is an enlarged view of a remaining portion taken
along Z-direction, to show another configuration of a remaining
portion formed (left) by cutting a portion of a rib. FIG. 20(a) is
an enlarged view showing a remaining portion having a tapered
deepest portion. FIG. 20(b) is an enlarged view showing a remaining
portion having a circular-arc deepest portion. FIG. 20(c) is an
enlarged view showing a remaining portion having a deepest portion
defined by a tilted surface.
[0183] As shown in FIG. 20(a), a remaining portion 150 of FIG.
20(a) has a cut portion width (dimension in X-direction) which
decreases as a cut portion depth (dimension in Y-direction) from
the tip end of the wall portion (rib) 131 increases. When viewed
from above along the Z-direction, the deepest portion 151 has a
tapered shape. In other words, when viewed from above, the
remaining portion 150 has the deepest portion 151 which is lower in
level than the tip end portion of the wall portion (rib) 131. The
deepest portion 151 has a tilted profile such that a depth of a
substantially center portion in X-direction is greatest.
[0184] As shown in FIG. 20(b), a remaining portion 153 has a
deepest portion 154 of a circular-arc shape when viewed from above
such that a cut portion depth (dimension in Y-direction) in a
center portion of a cut portion width (dimension in X-direction) is
greater.
[0185] As shown in FIG. 20(c), a remaining portion 156 has a
deepest portion 157 defined by a tilted surface such that a cut
portion depth increases in a direction from an upstream end portion
157a toward a downstream end portion 157b in a flow direction of
the washing water.
[0186] If bypass passages are formed by using the remaining
portions 150, 153, and 156, air bubbles with a relatively great
diameter, as well as air bubbles with a small diameter, can pass
through the deepest portions 151, 154, and 157. When using the
remaining portion 156 having the cut portion depth which increases
toward downstream end in the flow direction, the air bubbles
migrating along with the washing water can be surely captured by
the portion having the greater cut portion depth, and are allowed
to take a short cut to the upper passage through the remaining
portion 156.
Embodiment 10
[0187] FIG. 21 is a view showing another configuration of the heat
exchanger, and showing a configuration of the heat exchanger when
viewed from the base surface 130a side of the first passage forming
member 121. In the heat exchanger 10 (10I) shown in FIG. 21, an
opening dimension L2 of the remaining portion 136 is made different
among wall portions (ribs) 131a.about.131g. To be more specific,
the remaining portion 136 of the wall portion (rib) 131a located at
the lowermost side has a smallest opening dimension L2. The opening
dimension L2 of the remaining portion 136 is increased in the order
of the wall portions (ribs) 131b.about.131f, and the remaining
portion 136 of the wall portion (rib) 131g located at the uppermost
side has a greatest opening dimension L2. The other configuration
is identical to that of the heat exchanger 10H of Embodiment 9, and
will not be described in repetition.
[0188] In accordance with the heat exchanger 10I having such a
configuration, the flow speed of the washing water flowing along
the sinuous passage 135 and 145 can be increased, and a heat
transfer property or a carrying efficiency of the air bubbles can
be improved. To be specific, in some occasions, the washing water
as well as the air bubbles take a short cut through the bypass
passages 138 and 148 defined by the remaining portions 136. Since
the temperature of the washing water has not been raised adequately
in the vicinity of the water inlet 123a, the air bubbles generated
are less in the vicinity of the water inlet 123a. Therefore, the
opening dimension L2 of the remaining portion 136 formed on the
wall portion (rib portion) 131 defining the passage located at the
relatively lower side where the air bubbles generated are less is
set smaller. This suppresses the washing water from passing through
the remaining portion 136, and improves the flow speed of the
washing water. The wall portion (rib) 131 defining the passage
located at relatively upper side where the air bubbles are more
likely to be generated, have a relatively great opening dimension
L2. This allows the generated air bubbles to surely take a short
cut to the upper passage.
[0189] Although in the example shown in FIG. 21, the opening
dimension L2 is made different between the remaining portions 136
provided on all of the wall portions (ribs) 131, the present
invention is not limited to this. For example, the opening
dimension L2 of the remaining portions 136 of the two wall portions
(ribs) 131a and 131b located at the lower side is set to a smallest
and equal value, the opening dimension L2 of the remaining portions
136 of the two wall portions (ribs) 131f and 131g located at the
upper side is set to a greatest and equal value, and the opening
dimension L2 of the remaining portions 136 of the three wall
portions (ribs) 131c.about.131e located at the middle is set to a
predetermined equal value (predetermined value between the smallest
value and the greatest value). In brief, other setting may be made
so long as the opening dimension L2 of the remaining portion 136 of
the uppermost wall portion (rib) 131g is greater than the opening
dimension L2 of the remaining portion 136 of the lowermost wall
portion (rib) 131a, and the opening dimension L2 of the remaining
portion 136 of the wall portion (rib) 131 located at the upper side
is not smaller than the opening dimension L2 of the remaining
portion 136 of the wall portion (rib portion) 131 located at the
lower side, regarding the wall portions (ribs) 131b.about.131f
located between the wall portions (ribs) 131a and 131g.
Embodiment 11
[0190] FIG. 22 is a view showing another configuration of the heat
exchanger, and showing a configuration of the heat exchanger when
viewed from the base surface 130a side of the first passage forming
member 121. As shown in FIG. 22, in the heat exchanger 10(10J), the
remaining portions 136 are formed on a part of the wall portions
(ribs) 131 located at the upper side (upper two wall portions
(ribs) 131f, 131g), while the remaining portions 136 are not formed
on the other wall portions (ribs) 131 (131a.about.131e).
[0191] In accordance with the heat exchanger 10J having such a
configuration, in the passage located at the lower side where the
air bubbles are less likely to be generated, the flow speed of the
washing water is improved while preventing the washing water from
migrating through the remaining portion 136, while the air bubbles
generated in the upper passage where the temperature of the washing
water tends to be higher can migrate upward through the remaining
portion 136, and can be discharged quickly to outside through the
water outlet 123b.
[0192] The wall portions (ribs) 131 on which the remaining portions
136 are formed are not limited to an example shown in FIG. 22, in
which the remaining portions 136 are formed on the two wall
portions (ribs) 131. The number of wall portions (ribs) 131
provided with the remaining portions 136 may be suitably set
depending on the degree to which the air bubbles are generated in
the passages, the flow speed of the washing water, etc. That is,
the remaining portion 136 may be formed on only the uppermost wall
portion 131g, the upper three wall portions (ribs) 131e.about.131g,
or more wall portions (ribs) 131.
INDUSTRIAL APPLICABILITY
[0193] The present invention is applicable to a plate type heat
exchanger having a longer life which can suppress formation and
adhesion of scale and guide generated air bubbles quickly to a
water outlet while improving a heat transfer rate.
Reference Signs Lists
[0194] 1 sanitary washing device
[0195] 10, 10A.about.10J heat exchanger
[0196] 20, 120 plate heater
[0197] 20a, 120a first heat transfer surface
[0198] 20b, 120b second heat transfer surface
[0199] 20h heater line interval
[0200] 20k ceramic base body
[0201] 20p pattern
[0202] 20s heater line width
[0203] 21, 121 first passage forming member
[0204] 22, 122 second passage forming member
[0205] 23, 123 casing
[0206] 23a, 123a water inlet
[0207] 23b, 123b water outlet
[0208] 25 passage space
[0209] 25a upstream space
[0210] 25b downstream space
[0211] 30, 40 base portion
[0212] 31, 41, 61, 71 rib
[0213] 31a, 31b, 61a, 61b, 61c, 71a, 71b end portion
[0214] 37, 38, 47, 48, 65, 78, 83 throttle passage
[0215] 65a horizontal throttle passage
[0216] 65b vertical throttle passage
[0217] 67 agitating wall
[0218] 72, 88, 136, 150, 153, 156 remaining portion
[0219] 78a increased-width portion
[0220] 81, 81a, 81b, 81c buffer wall
[0221] 131, 131a.about.131g, 141 wall portion (rib)
[0222] 135, 135a.about.135h, 145 sinuous passage
[0223] 138, 148 bypass passage
* * * * *