Note: Descriptions are shown in the official language in which they were submitted.
124~963
HEAT UTILIZING SYSTEM USING
INTERNAL coMsusTIoN ENGINE
BACKGROUND OF THE INVENTION
-
1. Field of the Invention
This invention relates to a heat utilizing
system using an internal combustion engine, and more
_ particularly to a preferable one to be applied to a
`Xt/ system using a heat transfer medium contained in a
vessel, for feeding hot water, cooling or heating a
room in a house.
2. Description of the prior Art
In general, when an internal combustion
engine is used as a power plant, a shaft output
amounts to only 25 - 30% of the input fuel, and the
remainder is thrown away as unused. Even if waste
heat is to be recovered, expensive heat exchangers,
circulation pump and the like are required, and
additionally, heat radiating loss to the surroundings
and heat exchange loss are unavoidable, whereby the
working efficiency was low. In addition, the system
has been complicated and expensive because of the
piping connection system.
For this reason, there have been proposed
systems, in which an internal combustion engine being
. 25 used as a power plant is directly immersed in a vessel
containing therein a heat transfer medium to thereby
utilize the waste heat from the internal combustion
,~ r",~
~24(;963
engine. An example of such proposals is Japanese
Utility Model Application Publication No. 26102/82
published on June 7, 1982. However, in the system
described in this Publication, an internal combustion
S engine is secured to the bottom surface or a side wall
of a vessel and an output shaft portion of this
, internal combustion engine penetrates through the side
- wall to outside, whereby the noises of secondary
vibrations of the vessel due to the operation are
high so that the effects of reducing the noises and
vibrations obtained by the immersion of the engine
into the heat transfer medium (for example, water)
will be decreased to a considerable extent. In addi-
tion, it is difficult to absorb the vibrations and
displacement and secure the sealing (against the
water leakage) in the penetrating portion, and to
perform the maintenance works such as the inspection,
repair and the like of the internal combustion engine.
Furthermore, the noises are high from the fact that a
refrigeration machine or a compressor driven by this
internal combustion engine is exposed to outside.
Hence, necessity has been voiced for the noise control
measures for the system as a whole.
SUMMARY OF THE INVENTION
I
The present invention has its object the
¦ provision of a heat utilizing system for an internal
.
- 124~63
combustion engine, in which waste heat and the like
from the internal combustion engine are effectively
utilized and the noise control measures can be
easily conducted.
To achieve the above-described object, the
present invention contemplates that a vessel contain-
ing therein a heat transfer medium such as water and
provided at the top thereof with an opening is used,
and an internal combustion engine is supported by a
member such as a support ring, which is secured to the
opening of the vessel, at least a portion of the
internal combustion enqine is immersed in the heat
transfer medium, whereby the waste heat from the
internal combustion engine is effectively utilized
and the vibrations and noises imparted through the
vessel are arrested, and further, suitable anti-
vibration members can be interposed between the open-
ing of the vessel and the member secured to the open-
ing so as to facilitate the noise control measures.
To achieve the above-described object
further better, soundproof casings are provided for
covering machines and components such as a generator,
compressor and the like, which are driven by the
internal combustion engine, and at least a part of
the support portion for the internal combustion engine.
BRIEF DESCRIPTION OF THE DRAWINGS
I
,
12~963
--4--
Fig. 1 is a sectional view showing a first
embodiment of the present invention;
Fig. 2 is a sectional view showing a second
embodiment of the present invention;
Fig. 3 is a perspective view, partly
sectional, showing the essential portions of a third
embodiment of the present invention;
Figs.4 through 10 are sectional views
showing a fourth embodiment through a tenth embodiment
of the present invention;
Fig. 11 is a longitudinal perspective view
showing the essential portions of an eleventh embodiment
of the present invention;
Fig. 12 is a sectional view showing a
lS twelfth embodiment of the present invention;
Fig. 13 is a perspective view showing the
essential portions of the twelfth embodiment;
Fig. 14 is a general arrangement showing a
thirteenth embodiment of the present invention;
Fig. 15 is a sectional view showing a
fourteenth embodiment of the present invention;
Fig. 16 is a perspective view, partially
cut away, showing the essential portions of the
fourteenth embodiment;
Fig. 17 is a perspective view, partially
cut away, showing the essential portions of a fifteenth
embodiment of the present invention;
12~963
--5--
Fig. 18 is a sectional view showing a
sixteenth embodiment of the presnet invention;
Fig. 19 is a sectional view showing the
essential portions of a seventeenth embodiment of the
present invention;
' Fig. 20 is a sectional view showing a
eighteenth embodiment of the present invention;
Fig. 21 is a perspective view, partially
cut away, showing the essential portions of the
eighteenth embodiment; and
Fig. 22 is a sectional view showing a
nineteenth embodiment of the present invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
~ Description will hereunder be given of the
embodiments of the present invention with reference
to the drawings. Same reference numerals are used
throughout the figures of the respective embodiments
to designate same or similar component parts, so that
duplicated explanations will be omitted or simplified.
¦ 20 Fig. 1 shows the first embodiment of the
present invention. Referring to the drawing, a tank
` 1 comprises a cylindrical vessel or main body of tank
¦ 2 filled up with a heat transfer medium 8 (water in
this embodiment) and provided at the top thereof
j 25 with an opening and a closure 5 water-tightly coupled
1.
~24~963
to the top opening of this main body of tank 2 through
anti-vibration members 3 made of rubber or the like
and a seal member 4. The anti-vibration members 3
are provided in a gap formed in the vertical direc-
tion between the main body of tank 2 and the closure 5at a plurality of positions in the circumferential
direction, whereby the vibrations of the closure 5 are
absorbed and not imparted to the main body of tank
Furthermore, the seal member 4 is inserted along the
circumferential gap formed between the main body of
tank 2 and the closure 5 over the total circumference
to thereby form the tank 1 into a completely hermetic
construction. In this case, as the anti-vibration
members 3, when a circular shaped member is used on
lS the opening of the main body of tank 2 over the total
circumference thereof to perform the same function of
the seal member 4, the seal member 4 may be dispensed
with. If the anti-vibration member 3 is formed into
the circular shape described above, then the anti-
vibration member 3 can sufficiently support theclosure 5 and resist a force to move the closure 5.
On the other hand, respectively secured to
the closure 5 at the undersurface thereof with an
internal combustion engine 11, at least a portion of
which is immersed in the heat transfer medium 8 and
at the upper surface thereof with a compressor 13 as
being a driven component driven by the engine 11 and
covered on the upper surface thereof with a sound-
proof casing 12. The soundproof casing 12 is consti-
tuted by a cylindrical vibration control plate 15
secured to the upper surface of the closure 5 through
a plurality of bolts 14 and a sound absorbing material
16 adhesively attached to the inner surface of this
vibration control plate 15 and having heat insulation
properties. The interior of the soundproof casing 12
is communicated with the exterior thereof through a
filter 17 provided at a portion thereof. A heavy-
duty plate, e.g., a composite board made of ferrite,
lead, rubber or the like is used as the vibration
control plate 15 here. As the sound absorbing
material 16, for example, asbestos, glass wools,
urethane, honeycomb core or the like is used.
Connected to the engine 11 at an intake
port thereof with one end of an intake pipe 21, the
other end of which extends through the closure 5 and
projects into the soundproof casing 12 and at an
exhaust port thereof with one end of an exhaust pipe
22, the intermediate portion of which is immersed in
the heat transfer medium 8 and the other end of which
extends through the closure 5 and projects to outside.
The exhaust pipe 22 is inserted at the inter~ediate
portion thereof close to the engine 11 with a
radiator 23 for radiating the exhaust heat from the
engine 11 into the heat transfer medium 8 in the main
~2~963
body of tank 2,and provided at the forward end thereof
projecting from the closure 5 with a sound conditioner
24, whereby, when the engine 11 is operated, the
exhaust heat from the engine 11 is radiated from the
radiator 23, with the result that the heat transfer
medium 8 in the main body of tank 2 is heated.
Connected to the compressor 13 is a well
k~own heat pump circuit 30. The heat pump circuit 30
is of such an arrangement that a pipe 31 from one
connecting port of the compressor 13 is connected to
one end of a heat exchanger 32 in the tank 1, a pipe
33 from the other end of this heat exchanger 32
extends through the closure S and is connected to an
expansion valve 34, a pipe 35 from this expansion
valve 34 is connected to one end of a heat exchanger 36
at the other side, and a pipe 37 from the other end of
this heat exchanger 36 is passed through the filter 17
of the soundproof casing 12 and connected to the
other connecting port of the compressor 13.
As occasion demands, the main body of tank
2 is connected to the lower portion thereof with a
supply pipe 6 for city water as being the heat transfer
medium and at the upper portion thereof with an
outlet pipe 7 as being an outlet for the heat trans-
fer medium 8.
Description will hereunder be given of
action of this embodiment. When the compressor 13 is
124~63
g
driven by the start of the engine 11, then in the
heat pump circuit 30, the heating of the heat transfer
medium 8 in the tank 1 or the cooling of the room can
be effected in accordance with the well known refrig-
erating cycle.
On the other hand, when the engine 11 isstarted, the engine 11 is progressively raised in
temperature, and the exhaust gas from the engine 11 is
exhausted to outside through the exhaust pipe 22.
Then, the heat developed in the engine 11 is directly
and the exhaust heat from the engine 11 is through
the radiator 23 absorbed by the heat transfer medium 8
in the tank 1, respectively. As the result, the heat
transfer medium 8 in the tank 1 is raised in tempera-
ture by the radiation of heat from the heat pumpcircuit 30 in addition to the heat developed in the
engine 11 and the exhaust heat therefrom.
The heat transfer medium 8 thus raised in
temperature is utilized as the hot water feed, a
heat source for heating the room and directly as hot
water.
In consequence, according to this embodi-
ment, the compressor 13 is driven by the engine 11 to
effect the cooling of the room, simultaneously, through
the utilization of the heat developed in the engine 11,
the exhaust heat therefrom and the radiation of heat
from the heat pump circuit 30, the heat transfer
124~g63
--10--
medium 8 in the tank 1 is heated, and this heat
transfer medium 8 is utilized as the heat source for
the heating and cooling of the room and the hot water
feed, so that the energy can be effectively utilized,
5 and the cooling, heating the room and the water feed
can be performed by use of the singlç engine 11.
Furthermore, the engine 11 is se~ured to the
opening of the main body of tank 2 and the anti-
vibration members 3 are interposed between the closure
5 supporting the engine 11 and the main body of tank 2,
whereby mechanical vibrations and noises from the
engine 11 and the compressor 13 are not directly
imparted through the main body of tank 2 and further
there is no need for worrying about the leakage of the
heat transfer medium 8 from the engine mounting portion.
Furthermore, the engine 11 is immersed in
the heat transfer medium 8 in the hermetically sealed
tank 1 and the compressor 13 is covered by the
soundproof casing 12, so that the noises from the
engine 11 and the compressor 13 can be reduced from
the above point. Additionally, the provision of the
soundproof casing 12 is sufficient for only the outer
periphery of the compressor 13, so that the system as
a whole is rendered compact in size and can be
; 25 constructed inexpensively. Moreover, the air feed to
j the engine 11 is effected through the interior of
I the soundproof casing 12, whereby the sundproof
lZ~9~;3
--11--
casing 12 functions as the sound conditioner to
arrest the intake sound of the engine 11, thus result-
ing in further reduced noises from the system as a
whole.
Further, the soundproof casing 12 is con-
stituted by the vibration control plate 15 and the
; sound absorbing material 16 which is made of a heat
insulating material, so that the compressor 13 is
prevented from radiating the heat, thereby improving
the working efficiency of the heat pump.
Fig. 2 shows the second embodiment of the
present invention. In this embodiment, there is
used a soundproof casing 41 variable in capacity. ~he
soundproof casing 41 is of such an arrangement that a
sound absorbing material 43 made of a visco-elastic
material such as asphalt or the like is adhesively
attached to the inner surface of a vibration control
plate 42, and formed into a form of bellows generally
expandable or shrinkable in the vertical direction.
In consequence, in the second embodiment, in
addition to the advantages described in the first
embodiment, if the soundproof casing 41 is expanded
or shrunk in the vertical direction depending on the
natural number of vibrations of the driven component
such as the compressor 13 to thereby vary and set
the capacity thereof, then the noise component from the
compressor 13 can be absorbed.
~24~963
-12-
Additionally, in the above second embodi-
ment, the soundproof casing 41 is made variable in
capacity by forming it into a form of bellows, the
capacity variable construction need not necessarily
be limited to the above embodiment, the same effect
as aforesaid can be achieved by such a construction
that, for example, the soundproof casing is constituted
by an inner cylinder and an outer cylinder, which are
slidable on each other and one of the cylinders is
slided on the other to thereby vary the general
capacity, i.e., a telescopic construction. Further-
more, the sound absorbing material 43 may be provided
on the outer surface or the both inner and outer
surfaces of the vibration control plate 42 instead of
lS providing only on the inner surface as described in
the above embodiment. Particularly, if the sound
absorbing material 43 made of a viscoelastic material
is adhesively attached to the outer surface of the
vibration control plate 42, then the surface vibrations
of the vibration control plate 42 are absorbed, thus
further improving the soundproof effect.
Fig. 3 shows the essential portions of the
third embodiment of the present invention. In this
embodiment, a soundproof casing 51 is formed into a
double wall cylinder construction including an inner
cylinder 52 an outer cylinder 53, and a sound
conditioner 54 as sound conditioning passageways is
~ lZ~963
-13-
formed in a space between the inner cylinder 52 and
the outer cylinder 53. The sound conditioner 5~ is
constructed such that a space between the inner
cylinder 52 and the outer cylinder 53 is divided into
a suitable number of compaxtments by radial partition
walls 55 and these divided compartments 56, 57 and 58
are alternately communicated through communicating
pipes 59 and 60. With this arrangement, air introduced
through a duct 61 is led through the communicating
pipe 59 into the compartment 58 from the compartment
56 and subsequently, led through the communicating
pipe 60 into the compartment 57, whereby the air is
supplied from the intake pipe 21 to the engine ll
after following the repeated steps of throttling and
dispersion.
In consequence, in the third embodiment, in
addition to the advantages described in the first
embodiment, the intake noises of the engine ll can be
further reduced. Moreover, this sound conditioning
construction utilizes the space between the compressor
13 and the s~undproof casing 51, so that the system is
rendered compact in size and the double wall construc-
tion including the inner cylinder and the outer
cylinder can perfectly prevent the compressor 13
from radiating the heat, thus further improving the
working efficiency of the heat pump.
In addition, in the above third embodiment,
12~ ;3
-14-
if linings of asphalt or the like are applied to the
inner surfaces of the compartments 56, 57 and 58,
then the sound conditioning effect can be further
improved. Furthermore, the same arrangement as
described above is applicable to the exhaust side.
Fig. 4 shows the fourth embodiment of the
present invention. This embodiment is of such an
arrangement that a soundproof casing 71 is formed into
a double wall construction including an inner casing
72 and an outer casing 73, in which sound absorbing
materials are adhesively attached to the inner surfaces
of vibration control plates and sound conditioning
passageways are formed in the interior and the exterior
of the inner casing 72. More specifically, the interior
of the inner casing 72 is communicated through a filter
74 with the exterior thereof, a space between the
inner casing 72 and the outer casing 73 is communicated
through an introduction hole 75 with the exterior, an
end of the intake pipe 21 is located within the inner
casing 72 and an end of the exhaust pipe 22 is disposed
in the space between the inner casing 72 and the outer
casing 73.
In consequence, in the forth embodiment, in
addition to the advantages described in the first
embodiment, the exhaust noises from the engine 11 can
be further reduced. Moreover, since the spaces in the
soundproof casing 71 are utilized, there is no need to
.
124~963
--15--
provide a sound conditioner such as a muffler at the
forward end of the exhaust pipe 22 in particular, so
that the system is rendered compact in size and the
double wall construction including the inner cylinder
and the outer cylinder can perfectly prevent the
compressor 13 from radiating the heat, thereby further
improving the working efficiency of the heat pump.
In addition, in the above fourth embodiment,
if sound conditioners for repeating the steps of
throttling and dispersion as described in the third
embodiment are provided in the inner casing 72 and
the space between the inner casing 72 and the outer
casing 73, respectively, then the exhaust noises form
the engine 11 can be considerably reduced.
Fig. 5 shows the fifth embodiment of the
present invention. This embodiment is of such an
arrangement that an engine mounting portion 5A of the
closure 5, which is located at the center, is separated
from the other portion 5B, the engine mounting portion
5A is supported by the other portion 5B through anti-
vibration members 10 made of rubber or the like, and
further, the soundproof casing 12 is formed into a
double wall construction having two compartments
partitioned from each other hy an inner casing 12A and
an outer casing 12B. The interior of the inner casing
12A is communicated with atmosphere through the filter
17 and the space between the inner casing 12A and the
12~J~i!63
-16-
outer casing 12B is communicated with atmosphere
through a duct 18. Each of the casings 12A and 12B
comprises the cylindrical vibration control plate lS
secured to the upper surface of the closure S in a
manner to cover the compressor 13 and the sound
absorbing material 16 adhesively attached to the inner
surface of this vibration control plate 15 and having
heat insulating properties.
The engine 11 and the compressor 13 are
supported by the engine mounting portion 5A of the
closure 5, the intake pipe 21 of the engine 11 is
passed through a lip seal 26 provided in the engine
mounting poriton 5A and projected into the inner
: casing 12A, while the exhaust pipe 22 of the engine 11
is passed through a lip seal 27 provided in the other
portion 5B of the closure 5 and projected into the space
between the inner casing 12A and the outer casing 12B.
Further, a seal 38 is provided in a portion of the
closure 5, through which is extended a pipe 33
communicating the heat exchanger 32 in the tank 1 and
the expansion valve 34, both of which are included
in the heat pump circuit 30.
In consequence, in the fifth embodiment, in
addition to the advantages described in the fourth
: 25 embodiment, the mechanical vibrations fr~m the engine
11 and the compressor 13 are absorbed by the anti-
vibration members 10, the lip seals 26, 27 and the
12~9~3
17
seal 38, and further, the vibrations imparted to the
other portion 5B of the closure 5 are absorbed by the
anti-vibration members 3, so that no noises are
caused by the mechanical vibrations, and moreover, the
mechanical vibrations are further effectively prevented
from being imparted to the main body of tank 2.
; Furthermore, the outer casing 12B of the soundproof
casing 12 covers the closure 5 as a whole, so that
leaking noises from the closure 5 can be arrested,
thereby enabling to further reduce the noises in the
system as a whole.
In addition, in the above fifth embodiment,
the soundproof casing 12 may be provided only with
the inner casing 12A, and such an arrangement may be
adopted that the outer casing 12B covers only a
portion of the closure 5 as in the embodiment shown in
Fig. 4. Even with the above arrangement, the anti-
vibration effects by the anti-vibration members 10,
the lip seals 26, 27 and the seal 38 in the fifth
embodiment will not be reduced.
Fig. 6 shows the sixth embodiment of the
present invention. In this embodiment, the inner
casing 12A and the outer casing 12B of the soundproof
casing 12 in the fifth embodiment are formed into
forms of bellows expandable or shrinkàble in the
vertical direction and the capacity of the soundproof
casing can be varied and set depending on the natural
~24C~963
-18-
number of vibrations of the component such as the
compressor 13, so that the noise component from the
component such as the compressor 13 can be absorbed
in particular. In this case, a viscoelastic material
such as asphalt is preferable as the sound absorbing
material 16 similarly to the embodiment in Fig. 4.
-- Additionally, the variable capacity construction may be
a telescopic one.
Fig. 7 shows the seventh embodiment of the
present invention. In this embodiment, the engine 11
is supported by the opening of the main body of tank
2 of the tank 1 through an anti-vibration member 9
formed of a hollow ring-shaped rubber tube such as a
rubber tube of a bicycle tire and a support ring 81
having a heat insulating and sound absorbing construc-
tion, and a generator 91 as being a component driven
by this engine 11 is mounted. More particularly, the
support ring 81 is constructed such that a ring-shaped
outer shell plate 82 formed of a steel plate or a
plastic material and thickened substantially at the
central portion thereof is filled up with a foam
material such as foamable stylene or a heat insulating-
sound absorbing material 83 made of glass wool or the
like. This support ring 81 and the engine 11 are
solidly secured to each other through a plurality of
bolts 84. In this support ring 81, on à mounting
flange 85 haivng a ship form, there are provided
124~963
--19--
a starter 92, an oil filter 93 and an air filter 94
mounted at the forward end of the intake pipe 21 of
the engine 11, in addition to the generator 91.
A cap 95 is mounted so as to cover all of the above
components. This cap 95 comprises a vibration control
plate 96 formed of a steel plate or the like and a
. heat insulating-sound absorbing material 97 made of
glass wool or the like adhesively attached to the
inner surface of this vibration control plate 96.
A cord 99 of the generator 91 is led to outside through
an air suction pipe 98 formed through this cap 95.
A float 20 formed of a sealed vessel is
provided at the bottom of the engine 11 through an oil
pan 19. The buoyancy of this float 20 acts not only
on the engine 11 itself but also on the support ring
81 to relieve the load applied to the support ring 81.
: Furthermore, the exhaust pipe 22 of the engine 11 is
provided at the intermediate portion thereof with the
heat exchanger 23 and a muffler 24. This muffler 24 is
provided thereon with a drain hose 25 for draining
water drops condensed in the muffler 24 due to the
heat exchange with the heat transfer medium 8 to the
outside of the main body of tank 2.
In addition, the main body of tank 2 is
provided with a city water supply pipe 6 and an outlet
pipe 7 for the heat transfer medium 8 as necessary.
In the seventh embodiment with the above-
i~4C~963
-20
described arrangement, in addition to the advantages
described in the first embodiment, the tubular anti-
vibration member 9 is used, whereby the vibrations
from the engine 11 are not transmitted to the main
body of tank 2 at all, and the support given by the
anti-vibration member 9 is an equally distributed load
; for receiving the load in the ring form over the total
circumference, so that the coefficient of elasticity
of the rubber constituting the anti-vibration member 9
can be reduced to a considerable extent, and a further
effective vibration absorbing action and the sealing
action against the evaporation of moisture from the
heat transfer medium 8 can be simultaneously effected.
As the result of the vibration isolation thus achieved,
the mechanical strength required of the main body of
tank 2 from the viewpoint of anti-vibration is dispensed
with, so that the main body of tank 2 can be rendered
light in weight, and hence, produced inexpensively.
Further, the seals are simplified in construction,
the maintenance works are readily performed, and the
replacement of the oil filter 93 and the air filter 94,
which are subjected to frequent maintenance works can
be effected only by the removal of the cap 95.
Furthermore, the load borne by the support ring 81
can be relieved by the float 20 and the mechanical
strength of the support ring 81 can be reduced, so
that the support ring 81 can be rendered light in
9~;3
-21-
weight, and hence, produced inexpensively. In addition,
since the anti-vibration member 9 is formed into a ring
shape, the support ring 81 can be sufficiently supported
without securing the anti-vibration member 9 to the
S main body of the tank 2, and the support ring 81
can be prevented from rotation. Further, the support
ring 81 is filled up with the heat insulating and sound
~ absorbing material 83, 50 that the noise control can
be further satisfactorily performed. The driven
components and the like are received in the support
ring 81, so that the system can be reduced in its
tatal height. In working, the anti-vibration member 9
need not necessarily be limited to the rubber tube
shape, but, may be used a foamed sponge member or the
like, if the same spring constant can be obtained.
Fig. 8 shows the eighth embodiment of the
present invention. In this embodiment, the support
ring 81 in the seventh embodiment is partially immersed
in the heat transfer medium 8 and supported by a
plurality of resilient support arms 86, the cap 95 is
provided for covering the whole opening of the main
body of tank 2, and a heat-resistant seal 1~0 is
provided at a portion of the cap 95, through which the
exhaust pipe 22 extends. Furthermore, a float 28 in
this embodiment is of a so-called air suspension type,
in which the bottom thereof is opened into the heat
transfer medium 8. The vibrations of the engine 11
can be absorbed through the action of air sealed in
this float 28.
According to the eighth embodiment with the
124~63
-22-
above-described arrangement, in addition to the anti-
vibration and soundproof effects similarly to the
preceding embodiments, the support ring 81 is immersed
in the heat transfer medium 8, so that the system is
S reduced in its total height and the vertical vibration
absorbing action by the float 28 can be added.
In addition, in the above eighth embodiment,
the resilient support arms 86 may be replaced by rigid
links, in each of which opposite ends are rotatable
and at least one of the opposite ends is connected
through a slot, and further, replaced by a ring-shaped
resilient member, instead of a plurality of the arm-
shaped ones. In the ring-shaped resilient member is
adopted as described above, such disadvantages can be
effectively obviated that leak is caused or electric
contacts are deteriorated by the vapor of the heat
transfer medlum 8, which is attached to the generator
91 and the like.
Fig. 9 shows the ninth embodiment of the
present invention. In this embodiment, a coil 101 for
hot water feed is provided in the upper portion of the
heat transfer medium 8, and a condensor coil 111 of
~i the heat pump circuit 110 is provided in the lower
¦ portion of the heat transfer medium 8. More specifically,
when the water as being the heat transfer medium 8
¦ subjected to the direct heat exchange in the main body
¦ of tank 2 is not suited to the use, the indirect heat
124~9~3
-23-
exchange is conducted by use of the coil 101 for hot
water feed. A city water supply port lOlA is provided
at the bottom end of the coil 101 for hot water feed
and a hot water outlet port lOlB is provided at the top
end of the coil 101 for hot water feed. According
to the present invention, the engine 11 is immersed in
the heat transfer medium 8, whereby the temperature
in the upper portion of the heat transfer medium 8
reached substantially 85 to 95 due to the stratifica-
tion of temperature, whereby, even if the indirectheat exchange is conducted by use of the coil 101 for
hot water feed, an utility temperature level for hot
water feed (about 45C) can be sufficiently and readily
secured. The stratification of temperature in the tank
is very suitable for the radiation of heat by the
condenser coil 111 of the heat pump circuit 110 as shown
in Fig. 9. The condenser coil 111 is disposed in
the low temperature zone in the lower portion of the
main body of tank 2 and the engine 11 is located in
the upper portion of the main body of tank 2, whereby
the stratification of temperature is automatically
formed, so that the efficiencies of heat radiation
(heat exchange) of the condenser coil 111 and the engine
11 can be held high. Furthermore, the temperature up
to about 50C is obtained in the lower half portion
of the main body of tank 2 and the temperature up to
about 50C to 90C is obtained in the upper half
lZ~9~3
-24-
portion of the main body of tank 2, so that the proper
use can be selectively made depending upon the purpose.
The above-described arrangement, in which the
engine 11 is merely immersed in the heat transfer
medium 8 (for example, water), is not only convenient
for the stratification of temperature and heat recovery
but also the anti-vibration measures can be readily
and reliably taken. Moreover, the noise arresting
effect is high (because of the presence of the engine
11 and the like in the water) and no problem is found
with the maintenance works for the engine 11.
The heat pump circuit 110 is of a directly
expanded coolant type and of such an arrangement as will
be discribed below. A pipe 112 from an outlet of the
condenser coil 111 is connected to a port P of a
four-way valve 113, a pipe 114 from an inlet of the
condenser coil 111 is connected to a discharge port
13A of the compressor 13, and a solenoid valve 115 is
provided in the intermediate portion of this pipe 114.
A suction port 13B of the compressor 13 is connected
to one end of a pipe 116, the other end of which is
connected to a port Q of the four-way valve 113, and
a port A of the four-way valve 113 is connected to one
end of a pipe 117, the other end of which is connected
to one end of an outdoor heat exchanger 118 formed of
a so-called Fan-coil Unit. A pipe 119, one end of
which is connected to the other end of this outdoor
124~3963
-25-
heat exchanger 118, is provided in the intermediate
portion thereof with an expansion valve 120 and the
other end of the pipe 119 is connected to one end of
an indoor heat exchanger 121 formed of a Fan-coil Unit.
The other end of this indoor heat exchanger 121 is
` connected to one end of a pipe 122, the other end of
which is connected to a port B of the four-way valve
113. This port P of the four-way valve 113 is made
connectible to the port A or the port B, and the port
Q is made connectible to the port B or the port A.
Further, the intermediate portion of a pipe 114
connected to the discharge port 13A of the compressor
13, i.e., a portion of the pipe 114 between the solenoid
valve 115 and the discharge port 13A and the intermediate
portion of a pipe 112 from the outlet of the condenser
coil 111 can be communicated with or blocked from each
other through a solenoid valve 123.
With the above-described arrangement, in
order to operate the system for cooling the room, the
system should be operated in the same manner as the
conventional heat pump while the four-way valve 113 is
brought into the state indicated by solid lines, i.e.,
the port P is communicated with the port A and the port
Q is communicated with the port B. Since the condenser
coil 111 is immersed in the heat transfer medium 8 in
the main body of tank 2 in this case, the heat transfer
medium 8 can be raised in temperature while the room
124~963
-26-
is cooled by the indoor heat exchanger 121. When
the solenoid valve 115 is closed and the solenoid
valve 123 is switched to be opened, heat can be
radiated from the outdoor heat exchanger 118. If the
four-way valve 113 is switched to the direction
indicated by broken lines, i.e., the port P is communi-
cated with the port B and the port Q is communicated
with the port A, then, the operation of heating the
¦ room is performed.
¦ 10 Furthermore, in this embodiment, the exhaust
pipe 22 of the engine 11 is projected to outside
through the support ring 87, so that the cap 95 can be
~ easily mounted or demounted, and further, the exhaust
¦ noises can be reduced through the action of a heat
¦ 15 insulating-sound absorbing material 89. Further, a
! seal member 100 made of rubber or the like on the cap's
side is disposed at a portion where the cap 95 is in
contact with the support ring 87, so that the anti-
vibration and sound absorbing can be reliably effected
with the cooperation of the tubular anti-vibration
¦ ' member 9.
In addition, in this ninth embodiment, if
there is provided a separate heat absorbing coil
communicated with the pipes 112 and 114 at the outlet
, and the inlet of the condenser coil 111 and immersed
in the high temperature portion upwardly disposed in
the heat transfer medium 8, and the coolant in the heat
~2~6:3
-27-
pump circuit 110 is communicated to the aforesaid
separate coil, then, when the room heating power
of the heat pump circuit 110 is lowered owing to
lowered ambient temperature, the coolant is passed
through the heat absorbing coil disposed in the high
temperature portion, so that the room heating power
can be secured at a predetermined degree.
Fig. 10 shows the tenth embodiment of the
present invention. In this embodiment, the compresor
13 is installed instead of the generator 91 as being
the driven component in the embodiment shown in Fig. 7,
a heat pump circuit 150 different from one shown in
the embodiment in Fig. 9, an indoor heat exchanger 131
formed of the Fan-coil Unit is disposed in the room,
and the heat transfer medium 8 in the main body of
tank 2 is circulated. In other words, this embodiment
is an example where the operation of cooling and heating
the room by a so-called brine circulation. More
specifically, during heating of the room, a circulating
20 pump 133 provided on a pipe 132 at the inlet of the
indoor heat exchanger 131 is driven, the high temperature
portion of the heat transfer medium 8 in the tank, in
¦ which the stratification of temperature is effected,
is sucked from a pipe 134 of the high temperature
portion, fed in a direction indicated by an arrow mark
of a broken line through a manual three-way valve 135
and the pipe 132 to the indoor heat exchanger 131,
12~963
-28-
where the heat transfer medium 8 radiates the heat,
and returned to the main body of tank 2 through a
manual three-way valve 136 and a pipe 137 of the low
. temperature portion Meanwhile, in the heat pump
circuit 150, the coolant, which has been compressed
into a high-temperature high-pressure gas and gone out
. of the discharge port 13A of the compressor 13, is
passed through a pipe 151 to a condenser coil 152, where
the gas radiates the heat to be liquefied, passed
through a pipe 153 to a branched portion, where the
coolant is passed through a solenoid valve 154 and an
expansion valve 155 to be expanded, as indicated by an
arrow mark of a broken line, and led into an outdoor
radiator 156. In this case, a solenoid valve 157
provided in parallel to the solenoid valve 154 and the
expansion valve 155 is closed. The coolant, which
has entered the outdoor radiator 156, absorbes the
heat in the outdoor radiator 156, subsequently, is
passed through a pipe 158 to a branched portion, where
.
the coolant is passed through a short cut, i.e., a
solenoid valve 159 as indicated by an arrow mark of
. a broken line, is led through a pipe 160 on the suction
. side of the compressor and the suction port 13B to
the compressor 13~ where the coolant is compressed,
and thereafter, successively circulates the aforesaid
circuit. Since a solenoid valve 162 provided in a
- pipe 161 on the si~e of heat exchenge in the vicinity
1246~963
-29-
of the branched portion of the pipe 158 is closed in
this case, no coolant flows through an expansion valve
163 provided in a pipe 161, a coolant-brine heat
exchange coil 164 and a heat exchange return pipe 165.
On the other hand, during cooling the room,
the three-way valve 135 in the pipe 134 of the high
temperature portion is closed and the three-way valve
. 136 in the pipe 137 of the low temperature portion is
switched, so that the brine, which has been passed
through the indoor heat exchanger 131~, can flow to a
! circulation pipe 138. Furthermore, in the heat pump
circuit 150, the solenoid valve 154 on the side of the
expansion valve 155 positioned at the inlet of the
outdoor heat radiator 156 is closed and the solenoid
valve 157 provided in parallel thereto is opened, the
solenoid valve 159 on the short cut's side is closed,
and the solenoid valve ~62 on the side of the heat
exchange coil is opened. With the above arrangement,
the coolant, which has been expanded in the
expansion valve 163, flows in a direction indicated by
. ~ an arrow mark of a solid line to the coolant-brine
heat exchange coil 164, where the coolant absorbs the
heat to cool the brine in the pipe 132 on the brine's
side, returns to the suction port 13B of the
compressor 13, and circulates through the circuit
passing through the condenser coil 152 and reaching
the heat exchange coil 164 in the same manner as
124~963
30-
j described above. The brine in the pipe 132 on the
indoor side, which has been cooled by the heat
exchange coil 164, is driven by the pump 133 to pass
the indoor heat exchanger 131 and cools the room,
thereafter, is passed through the three-way valve 136
¦ and the pipe 138, cooled again in the heat exchange
coil 164, and circulates in the direction indicated by
the arrow marks of solid lines in the same manner as
described above.
During the room cooling operation as
described above, when the heat transfer medium 8 in
the main body of tank 2 is heated to an excessively
high temperature as the result of continuous operation
of the engine 11, the following process should be
followed. Namely, the three-way valve 135 in the pipe
134 of the high temperature portion is switched to
connect the pipe 134 of the high temperature portion
to a pipe 141 for heat radiation, a circulation pump
142 is operated to feed the high temperature heat
2~ transfer medium 8 to a radiator 143, where the heat
transfer medium is cooled, and the heat transfer
medium is returned to the lower portion of the main
body of tank 2 through a return pipe 144.
The hot water feed in~this embodiment is
conducted in the same manner as in the embodiment
shown in Fig. 9.
According to the tenth embodiment with the
,,,
~z46~963
-31-
above-described arrangement, in addition to the
advantages described in the ninth embodiment, the
cooling and heating of the room at a high efficiency
can be effected by direct use of the heat transfer
medium 8 in the main body of tank 2.
Fig. 11 shows the essential portions of the
~ eleventh embodiment of the present invention. This
i embodiment illustrates the case where the output
shaft of the engine 11 is laid in the horizontal
direction. In this case, the compressor 13 or the
generator 91 as being the driven component should be
driven by use of a belt 170 as shown in the drawing.
With this arrangement, the reduction or speed up
ratio of the driven component can be desirably set.
Furthermore, when the compressor 13 is the driven
! component, the rotary shaft of the compressor 13 is
connected to the h,orizontal output shaft of the engine
11 and the compressor 13 may be immersed in the heat
transfer medium together with the engine 11, because
the electrical insulation and the like can be
' dispensed with. With this arrangement, it is advan-
tageous that the exhaust heat from the compressor 13,
the surface temperature of which reaches about 80C,
can be effectively recovered.
~ .
3963
Figs. 12 and 13 show the twelfth embodiment
of the present invention. In this embodiment, on a
horizontal surface 2A formed on the upper peripheral
wall of the main body of tank 2 and within a vertical
surface 2B upwardly bent frorn the horizontal surface
2A, an annular support ring 181 is rested on the
anti-vibration member 9 similar to that shown in the
embodiment of Fig. 9, which is mounted over the
total circumference of the horizontal surface 2A,
and the closure 5 is mounted on this support ring 181.
As shown in Fig. 13, the support ring 181 is
constructed such that four connecting plates 183 are
integrally formed at every 90 on the inner peripheral
surface of an annular member 182 rested on the anti-
vibration member 9. Outer end portions of foursupport arms 186 radially projected from a mounting
. plate 18~ through bolts 185 are connected to the
connecting plate 183 through pins 187. The mounting
, plate 184 ~s a whole is formed of a floating boat
which floats on the liquid level of the heat transfer
medium 8, provided at the undersurface thereof with
an engine 11 generally immersed in the heat transfer
medium 8 and provided on the upper surface thereof
with a compressor 13 of the heat pump circuit 30,
which is driven by the engine 11 and an oil filter 93.
In consequence, loads acting upon the support arms 186
a~d the support rin~ 181 due to the loads of the
12~j963
-33-
engine 11, the compressor 13 and the like are relieved
by a buoyancy generated in the mounting plate 184.
The lower peripheral wall of the closure 5
is outwardly bent into a horizontal surface 5C so as
to be mounted on the support ring 181, and further,
downwardly bent into a vertical surface 5D so as to
be loosely fitted to the outer side of the vertical
surface 2B of th-- main body of tank 2. Further, an
inspection window 5E is formed at the center of the
closure 5, i.e., a position opposed to the compressor
13 and the oil filter 93, and an inspection hatch 175
is openably secured to the inspection window 5E.
With this arrangement, the works of inspection,
replacement and the like of the oil filter, for which
the frequency of maintenance is high, are facilitated.
Furthermore, the heat exchanger 36 in the
heat pump circuit 30 in thi$ embodiment does not
undergo heat exchange with air as shown in the embodi-
, ment of Fig. 1, but, undergoes heat exchange with well
water or a coolant in a fan coil unit, not shown, inliving quarters, and the well water or the like enters
the heat exchanger 36 through a return pipe 39.
Further, in this embodiment, there are
provided a hot water feeding system by use of the hot
water feed coil 101 and a room heating system by a
brine circulation in the same manner as in the embodi-
ment of Fig. 10. In order to effect room heating by
12~9~3
-34-
the brine circulation, hot water in the main body of
tank 2 should be circulated from the pipe 137 on the
low temperature's side into the main body of tank 2
through the fan coil unit, not shown, through the
agency of the circulation pump 133 as shown in the
example. In this case, the pipe 134 on the high
temperature's side is provided on the upper wall of
j the main body of tank 2, a pipe 139 in the medium
¦ temperature range is provided on the wall of the
¦ 10 central portion, and these pipes are switched to
each other by a three-way valve 140, so that the room
heating can be operated efficiently. More specifically,
j when a high heat quantity is required for the rise of
room heating, hot water is sent from the pipe 134 on
lS the high temperature's side to effect quick room
heating, and, when the steady conditions are reached,
the three-way valve 140 is switched to send low
temperature warm water from the pipe 139 in the
medium temperature range, an economical operation of
room heating can be carried out, thus enabling to save
energy.
In addition, a drain pot 29 is provided in
the intermediate portion of the exhaust pipe 22 of
the engine 11, the drainage ac~umulated is discharged
through a drain hose 25.
According to the twelfth embodiment with
the above-described arrangement, in addition to
12~963
-35-
obtaining of the effects similar to those in the
¦ embodiments having the arrangements corresponding to
the twelfth embodiment, when the room heating is to
be effected, the pipe 134 on the high temperature's
side and the pipe 139 in the medium temperature range
¦ are provided in accordance with the temperature
¦ stratification of the heat transfer medium, and, if
these pipes are switched to each other by a change-
over valve 133, then the room heating can be operated
efficiently.
Since the mounting plate 184 provided with
the engine 11 and the compressor 13 is formed of a
floating boat, the loads acting on the support arms
186 and the support ring 181 due to the loads of the
engine 11 and the compressor 13 can be relieved by
the buoyancy generated in the mounting plate 184.
Since the forward ends of the support arms
186 are connected to the annular support ring 181,
. which is supported by the total circumference of the
main body of tank 2 through a hollow ring-shaped anti-
vibration member 9, the loads acting in the vertical
direction becomes a uniformly distributed load on
the total circumference of the main body of tank 2,
whereby these occurs no concentration of loads, so
. 25 that the spring constant of the anti-vibration member
9 can be reduced, thereby enabling to achieve the
sealing effect for preventing the leakage of the
~2~963
j -36-
heat transfer medium 8 and the leakage of noises
from the engine 11, the compressor 13 and the like
: and to positively prevent the secondary vibrations to
the main body of tank 2.
Furthermore, this leads to the fact that a
stationary system of the main body of tank 2 having
. the heat transfer medium 8 and a vibratory system
having the engine 11, the compressor 13 and the like
are insulated from each other by the total circumfer-
ence of the main body of tank 2 through the anti-vibra-
tion member 9, so that the pipes and the like can avoid
damages caused by the different vibratory systems.
For example, the pipes for the coolant to the compressor
13 are included in the same system as the vibratory
. 15 members of the engine 11, so that such an accident as
the leakage of coolant can be eliminated.
Further, the provision of the inspection
hatch 175 in the closure 5 makes it possible to
facilitate the works of component maintenance,
. 1 20 particularly the works replacing the oil ~ilter 93
with new one and the like, when necessary.
In working, if the pipe 134 on the high
temperature's side and the pipe 139 in the medium
temperature range during room heating are arranged
in the same manner as in the thirteenth embodiment
shown in Fig. 14, then the same effects are expectable.
This arrangement m~kes it p~ssible to ellminate
~246~63
-37-
necessity for providing the ports connected to the
pipes 134 and 139 on the main body of tank 2, so that
the heat transfer medium can be prevented from leaking
out of the main body of tank 2. Furthermore, the
pipe 134 on the high temperature's side can suck only
¦ the high temperature water, which has overflowed into
a trough 146, so that the water thus sucked can be
held at high temperature.
Figs. 15 and 16 show the fourteenth embodi-
ment of the present invention. In this fourteenth
embodiment, a hollow prismatic tube-shaped support
ring 190 and cushion materials 195 are interposed
between the horizontal surface 2A of the main body of
tank 2 and the horizontal surface 5C of the closure 5,
~15 and the intake pipe 21 and the exhaust pipe 22 of the
¦engine 11 are led to outside of the tank 1 through
support ring 190. As shown in Fiq. 16, the support
ring 190 is constructed such that four L-shaped
connecting plates 192 supporting the outer ends of
the support arms 186 through bolts 196 are secured at
every 90 to the inner peripheral portion of a hollow
prismatic tube-shaped annular member 191 rested on the
anti-vibration~member 9. Through-holes l91A and l91B,
both of which penetrate through the inner and outer
walls of the annular member l9l are formed in the
annular member l9l at positions opposed to each other.
~¦ A suction pipe 197 connected to the intake pipe ~1 is
124~963
-38-
led to outside through one l91A of the through-holes,
and an exhaust pipe 22 is led to outside through the
other l91B of the through-holes.
In consequence, in the fourteenth embodiment,
1 5 in addition to the effects described in the twelfth
¦ embodiment, the intake pipe 21 and the exhaust pipe 22
of the engine 11 are led to outside of the tank 1
through the support ring 190, so that the closure 5
can be easily opened. For this, the maintenance works
for the internal components, particularly, the works
of inspecting and replacing the oil filter 93 can be
facilitated. Moreover, there is no need for the
closure 5 to hold the intake pipe 21 and the exhaust
pipe 22, so that the closure 5 can be formed of a
light material having a comparatively low rigidity
such for example as a film-like material, thus proving
economical. However, if the closure 5 is formed of a
rigid material, then another component such for example
as an external evaporator 36 can be rested on the
upper surface of the closure 5.
In this case, if muffler means 201 and 202
are provided in the support ring 190 as in the fifteenth
embodiment of the present invention as shown in Fig. 17,
then the intake and exhaust noises from the engine 11
25 can be arrested. These muffler means 201 and 202 have
constructions similar to each other. For example, the
¦ ~ muffler means 201 is constructed such that a plurality
1~4~3963
-39-
of muffler compartments 204, 205 and 206, which are
divided by partition plates 203, are provided in the
support ring 190, these muffler compartments 204, 205
and 206 are successively communicated with each other
by constricted pipes 207 and 208, and constrictions
and diffusions are repeated to arrest the noises while
the intake air and the exhaust gas pass through these
muffler compartments 204, 205 and 206. In conse~uence,
in this embodiment, the muffler means are formed in
the support ring 190, so that the system as a whole can
be rendered compact in size.
Fig. 18 shows the sixteenth embodiment of
the present invention. In this sixteenth embodiment,
the vertical surface 2B of the main body of tank 2
is extended upwardly and the closure 5 is directly
coupled to the upper end edge of the vertical surface
2B. Furthermore, the heat transfer medium 8 is
contained upwardly of the horizontal surface 2A of the
main body of tank 2, and the anti-vibration member 9
and the support ring 181 ~are immersed in the heat
transfer medium 8.
In consequence, in the sixteenth embodiment,
in addition to the effects described in the embodiment
shown in Fig. 12, such an advantage can be offered
that, if the closure 5 is made of synthetic rubber,
then the tank 1 can be tightly closed with no seal
. ~ being inserted into the coupling portion between the
~: ,~ .
12~g63
-40-
main body of tank 2 and the closure 5. Farthermore,
the anti-vibration member 9 and the support ring 181
are immersed in the heat transfer medium 8, so that
the anti-vibration and soundproof effects can be
further enhanced.
¦ In the respective embodiment described above,
¦ the upper portion of the main body of tank 2 is bent
outwardly to form the horizontal surface 2A, onto
which the anti-vibration member 9 is to be mounted,
however, as shown in the seventeenth embodiment of the
present invention in Fig. 19 for example, a horizontal
receiver 2C projecting inwardly from the inner periph-
eral wall of the main body of tank 2 may be integrally
formed on the main body of tank 2. This arrangement
makes it possible to form the main body of tank 2
into a perfect tubular form, so that the manufacture
thereof can be facilitated and economical.
Figs. 20 and 21 show the eighteenth embodi-
ment of the present invention. This eighteenth
embodiment is constructed such that the arrangement of
the heat pump circuit in the embodiment shown in Fig.
10 is replaced by the arrangement of the embodiment
shown in Fig. 12 for example, a seal member 210 formed
of an elastic rubber ring is interposed between the
¦ 25 support ring 81 and the mounting flange 85 and fixed
¦ by means of bolts 84, and a heat transfer medium
¦¦ separ~tion-insulation chamber ~11 insulated Erom the
-41-
¦ steam or the like of the heat transfer medium 8 is
¦ formed upwardly of the mounting flange 85. Further-
more, the support ring 81 is vertically formed therein
with a through-hole 81A, through which the exhaust
s pipe 22 of the engine 11 is led to outside, and also
i formed therein with a communication hole 81B, through
¦ . which a coolant pipe of the compressor 13 and a wiring
of an engine auxiliary machine such as a starter 92
are led to outside. On the other hand, a cushion
member 212 is provided in the abutting portion between
the closure 5 and the support ring 81, and the
closure 5 is formed at the upper surface thereof with
an air intake port 214 having an air filter 213.
Air is taken into the engine 11 through this air
. 15 intake port 214. In this case, the air intake port
214 may be provided in the support ring 81 as shown in
the ninteenth embodiment of the present invention in
Fig. 22.
In these eighteenth and ninteenth embodiments,
there is provided the heat transfer medium separation-
insulation chamber 211 comprising the mounting flange
85, the seal member 210, the support ring 81 and the
. cap 95, and engine auxiliary machines, such as the
: compressor 93, the starter 92 and electrical equipment,
not shownf are housed in this separation-insulation
chamber 211, so that, in addition to the effects
¦ described in the embodiment sho~n in Fig 1~,
124~963
-42-
the engine auxiliary machines such as a starter 92 is
insulated from the atmospheric vapor of the heat
`transfer medium such for example as water to thereby
protect the starter 92 from being subjected to
moisture in the atmospheric vapor. Moreover, the
1 support ring 81, the mounting flange 85 and the like
¦ reliably define the foundary between the interior
and the exterior of the main body of tank 2 due to the
loads of the engine 11 and the like, so that the
i 10 reduction of the water as being the heat transfer
medium 8 in the main body of tank 2 due to the
evaporation can be prevented. As compared with the
, embodiment shown in Fig. 15 and the like, in the
,¦ eighteenth and ninteenth embodiments, the system as a
lS whole can be rendered compact in size and the exhaust
pipe 22 can be led upwardly, whereby the protruded
portion in the radial direction can be removed, so
that the area projected to a plane can be made-.to be
an area of the main body of tank 2.
Further, in the eighteenth and ninteenth
. embodiments, the interior of the tank 1 is separated
I in the vertica~ direction by means of the support
ring 81, the mounting f~ange 8~5 and the like, whereby
the heat transfer medium separation-insulation chamber
211 is formed in the upper portion of the tank 1.
However, in order to form the separation-insulation
chamber 211, it is not always necessary to separate
`- 12~g63
-43-
the interior of the tank 1 in the vertical direction.
For example, in the case of supporting the mounting
flange 85 on the support ring 81 through a plurality
of arms, a casing or the like covering the compressor
13, the starter 92 and the like may be secured to the
upper surface of the mounting flange 85. In this
case, to prevent the reduction of the water in the
main body of tank 2 due to the evaporation, it is
desirable to separately prepare a closure being tightly
closed. Furthermore, the support ring 81 and the
mounting flange 85 are not separate and may be integral-
ly formed.
In addition, in the respective embodiments
described above, the engine 11 is substantially
wholly immersed in the heat transfer medium 8 in the
tank 1, however, the engine 11 need not necessarily
be substantially wholly immersed in the heat transfer
j medium 8 because the tank 1 has the sealed construc-
tion. Even when a part of the engine 11 is immersed
in the heat transfer medium B, the heat utilizing and
noise reduction of the engine 11 can be effected.
Needless to say, if the engine 11 is substantially
¦ wholly immersed in the heat transfer medium 8 in the
tank, then a higher efficiency can be attained because
the substantially total amount of the heat from the
engine 11 can be utilized directly for heating the
heat transfer medium B. Furthermore, accordin~ to
124C3963
-44-
the present invention, the component driven by the
engine 11 need not necessarily be limited to the
compressor 13 or the generator 91, but, any other
component such as a pump may be adopted.
As has been described above, the present
invention is advantageous in that the exhaust heat
and the like from the internal combustion engine can
be effectively utilized and the anti-vibration and
noise arresting measures can be readily carried out.
