U.S. patent application number 12/976230 was filed with the patent office on 2011-06-23 for device and method for an efficient surface evaporation and for an efficient condensation.
Invention is credited to Oliver Kniffler, Holger Sedlak.
Application Number | 20110146316 12/976230 |
Document ID | / |
Family ID | 41056944 |
Filed Date | 2011-06-23 |
United States Patent
Application |
20110146316 |
Kind Code |
A1 |
Sedlak; Holger ; et
al. |
June 23, 2011 |
Device and Method for an Efficient Surface Evaporation and for an
Efficient Condensation
Abstract
An evaporator or a condenser includes a surface on which the
operating liquid is arranged. Further, turbulence generators are
provided to generate turbulences in the operating liquid located on
the operating surface. In the condenser, alternatively or
additionally, a laminarizer is present to make the vapor stream
laminar provided by the compressor. On the evaporator side, the
evaporation efficiency is increased and, on the condenser side, the
condenser efficiency is increased, which may be used for a
substantial reduction in size without loss of power of these
components, in particular for a heat pump for heating a
building.
Inventors: |
Sedlak; Holger;
(Lochhofen/Sauerlach, DE) ; Kniffler; Oliver;
(Sauerlach, DE) |
Family ID: |
41056944 |
Appl. No.: |
12/976230 |
Filed: |
December 22, 2010 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
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PCT/EP09/04519 |
Jun 23, 2009 |
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12976230 |
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Current U.S.
Class: |
62/238.6 ;
165/109.1 |
Current CPC
Class: |
F25B 30/02 20130101;
F28F 13/182 20130101; F25B 43/043 20130101; F28F 13/12 20130101;
F25B 39/00 20130101 |
Class at
Publication: |
62/238.6 ;
165/109.1 |
International
Class: |
F25B 27/00 20060101
F25B027/00; F28F 13/12 20060101 F28F013/12 |
Foreign Application Data
Date |
Code |
Application Number |
Jun 23, 2008 |
DE |
102008029597.3 |
Jul 2, 2008 |
DE |
10 2008 031 300.9 |
Claims
1. An evaporator for evaporating an operating liquid, comprising:
an evaporator surface on which the operating liquid to be
evaporated is to be arranged; and a plurality of turbulence
generators which are implemented to generate turbulences in the
operating liquid to be evaporated on the evaporator surface.
2. The evaporator according to claim 1, further comprising: an
evaporator housing in which the evaporator surface is arranged and
is implemented to maintain a pressure in the evaporator housing at
the evaporator surface which is such that the operating liquid,
when the operating liquid reaches the evaporator surface, comprises
a boiling temperature or a temperature which is in a range which
extends from a temperature equal to the boiling temperature -10
Kelvin up to a temperature equal to the boiling temperature +10
Kelvin.
3. The evaporator according to claim 2, wherein the evaporator
housing comprises an intake for the operating liquid and a
discharge opening for a vapor of the operating liquid, wherein the
discharge opening is implemented such that it may be coupled with
an input of a compressor for compressing the vapor.
4. The evaporator according to claim 1, wherein the evaporator
surface is inclined in an operating position, wherein the operating
liquid is supplied to the evaporator surface such that the
operating liquid flows from an intake to a drain from the
evaporator surface due to gravity.
5. The evaporator according to claim 4, wherein the evaporator
surface is pyramid-shaped, conical, funnel-shaped or in the shape
of an inclined plane, wherein the inclined plane may be level or
non-level.
6. The evaporator according to claim 4, wherein an intake for the
operating liquid is surrounded by the evaporator surface such that
the operating liquid flows at several sides of the intake across
the evaporator surface.
7. The evaporator according to claim 1, wherein the turbulence
generators are implemented by a member separated from the
evaporator surface or by elevations or indentations at the
evaporator surface.
8. The evaporator according to claim 1, wherein the turbulence
generators are implemented by wire sections on the evaporator
surface, which are attached and arranged with respect to the
evaporator surface such that a flow direction of the operating
liquid intersects a direction in which the wire sections are
arranged.
9. The evaporator according to claim 8, wherein the turbulence
generators are formed as spiral-shaped wire sections connected to
each other, wherein a distance between two neighboring wire
sections in the flow direction of the operating liquid is greater
than the diameter of a wire section and smaller than three times
the diameter of the wire section.
10. The evaporator according to claim 7, wherein the elevations or
the indentations are dimensioned such that an impinging operating
liquid may be set into turbulence.
11. The evaporator according to claim 10, wherein the elevations
comprise a height in which they extend across the surface which is
higher than a level of the operating liquid on the evaporator
surface in the operation of the evaporator.
12. The evaporator according to claim 1, wherein the turbulence
generators are implemented such that a water current on the
evaporator surface comprises turbulences which comprise at least
20% of the complete liquid current on the evaporator.
13. A condenser for condensing an evaporated operating liquid,
comprising: a condenser surface on which an operating liquid is to
be arranged; a plurality of turbulence generators which are
implemented to generate current turbulences in the operating liquid
located on the condenser surface; or a laminarizer which is
implemented to make a vapor current directed to the condenser
surface laminar so that a vapor made laminar by the laminarizer
impinges on the operating liquid.
14. The condenser according to claim 13, comprising: a condenser
housing in which the condenser surface is arranged and implemented
to maintain a pressure in the condenser housing at the condenser
surface which is such that a condensed operating liquid comprises a
predetermined minimum temperature.
15. The condenser according to claim 14, wherein the minimum
temperature is higher than or equal to 22.degree. C.
16. The condenser according to claim 13, wherein the condenser
surface is inclined in an operating position, wherein the liquid is
supplied to the condenser surface such that the liquid flows from
an intake to a drain of the condenser surface due to gravity.
17. The condenser according to claim 16, wherein the evaporator
surface is pyramid-shaped, conical, funnel-shaped or in the form of
an inclined plane which may be level or non-level.
18. The condenser according to claim 16, wherein an intake for the
liquid to the condenser surface is surrounded by the condenser
surface such that the liquid flows across the condenser surface at
several sides of the intake.
19. The condenser according to claim 13, comprising both the
turbulence generators and also the laminarizer, the laminarizer
being arranged such that the laminarized vapor hits turbulences of
the liquid generated by the turbulence generators on the condenser
surface.
20. The condenser according to claim 13, comprising both the
turbulence generators and also the laminarizers, wherein both the
turbulence generators and also the laminarizers are formed by the
same element.
21. The condenser according to claim 20, wherein the element
comprises a fiber tissue protruding beyond a liquid level on the
condenser surface.
22. The condenser according to claim 21, wherein the fiber tissue
is a plastic wool with non-absorbing fibers or a metallic wool.
23. The condenser according to claim 13, wherein a distance of the
laminarizer from the operating liquid on the condenser surface,
which the laminarized vapor has passed, is smaller than 25 mm.
24. The condenser according to claim 23, which is formed of
honeycomb material or a tube material with laminarizer cells,
wherein a length of a laminarizer cell is implemented such that, in
proportion to a diameter of the laminarizer cell, on the output
side a gas current is generated which is at least half as turbulent
as a gas current which is fed into the laminarizer.
25. The condenser according to claim 24, wherein a laminarizer cell
is longer than 10 mm if it comprises a diameter greater than 5 mm
and is longer than 1 mm if it comprises a diameter smaller than 1
mm.
26. The condenser according to claim 13, wherein a liquid reservoir
exists into which a liquid flowing off the condenser surface is
introduced and from which cooler liquid, compared to the run-off
liquid, is supplied to the condenser surface as a liquid
current.
27. The evaporator or condenser according to claim 1, which is
implemented for being used in a heat pump.
28. The evaporator or condenser according to claim 27, which is
implemented for the use of a heat pump for heating a building for
buildings with less than 10 apartment units.
29. A evaporator or condenser, wherein the operating liquid is
water.
30. A heat pump, comprising: an evaporator for evaporating an
operating liquid, comprising: an evaporator surface on which the
operating liquid to be evaporated is to be arranged; and a
plurality of turbulence generators which are implemented to
generate turbulences in the operating liquid to be evaporated on
the evaporator surface; a condenser for condensing an evaporated
operating liquid, comprising: a condenser surface on which an
operating liquid is to be arranged; a plurality of turbulence
generators which are implemented to generate current turbulences in
the operating liquid located on the condenser surface; or a
laminarizer which is implemented to make a vapor current directed
to the condenser surface laminar so that a vapor made laminar by
the laminarizer impinges on the operating liquid; and a compressor
for compressing operating liquid evaporated by the evaporator,
wherein the compressor is coupled to the condenser in order to feed
compressed vapor into the condenser, and wherein the condenser
further comprises a heating forward flow for supplying warm heating
liquid and a heating return flow for supplying cold heating liquid
to the condenser.
31. A method for evaporating an operating liquid, comprising:
arranging an operating liquid to be evaporated on an evaporator
surface; and generating turbulences in the operating liquid to be
evaporated on the evaporator surface.
32. A method for condensing an evaporated operating liquid,
comprising: arranging operating liquid on a condenser surface;
generating turbulences in the operating liquid arranged on the
condenser surface; or making a vapor current directed to the
condenser surface laminar so that vapor made laminar hits the
operating liquid.
Description
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] This application is a continuation of copending
International Application No. PCT/EP2009/004519, filed Jun. 23,
2009, which is incorporated herein by reference in its entirety,
and additionally claims priority from German Applications Nos. DE
102008029597.3, filed Jun. 23, 2008 and DE 10 2008 031 300,9, filed
Jul. 2, 2008, which are all incorporated herein by reference in
their entirety.
BACKGROUND OF THE INVENTION
[0002] The present invention relates to evaporating or condensing
on surfaces and in particular to an application of evaporating and
condensing to surfaces in heat pumps.
[0003] A liquid layer, as it, for example, occurs in an evaporator
of a heat pump, executes, due to the typical layering which may be
observed with liquids and in particular with water as an operating
liquid, a heat distribution which means that in the evaporator the
top portion is cooled while the bottom portion of the layer
virtually has the same temperature as the operating liquid as it is
supplied from a heat source.
[0004] With condensers for heat pumps the situation is similar.
Here, the compressed and thus heated-up vapor of operating liquid,
like, for example, water vapor, when water is used as the operating
liquid, meets a "cold" liquid layer. This leads to only the surface
of the liquid layer being heated up in the condenser while the
bottom portion of the liquid layer in the condenser which is not
directly in contact with the vapor is not heated up.
[0005] Apart from that, with the evaporator of a heat pump there is
still the problem that the compressed and heated-up vapor may be
overheated, which means that in spite of the fact that the vapor
meets the liquid to be heated up the heat transmission from vapor
into liquid is limited.
[0006] All of these problems lead to the fact that the efficiency
when evaporating or condensing is reduced. In order to still
generate a heat pump, for example with sufficient power, thus the
cross-sectional area of the evaporator or the cross-sectional area
of the condenser has to be very large.
SUMMARY
[0007] According to one embodiment, an evaporator for evaporating
an operating liquid, may have an evaporator surface on which the
operating liquid to be evaporated is to be arranged; and a
plurality of turbulence generators which are implemented to
generate turbulences in the operating liquid to be evaporated on
the evaporator surface.
[0008] According to another embodiment, a condenser for condensing
an evaporated operating liquid may have a condenser surface on
which an operating liquid is to be arranged; a plurality of
turbulence generators which are implemented to generate current
turbulences in the operating liquid located on the condenser
surface; or a laminarizer which is implemented to make a vapor
current directed to the condenser surface laminar so that a vapor
made laminar by the laminarizer impinges on the operating
liquid.
[0009] Another embodiment may be an evaporator or condenser,
wherein the operating liquid is water.
[0010] According to another embodiment, a heat pump may have an
evaporator for evaporating an operating liquid which may have an
evaporator surface on which the operating liquid to be evaporated
is to be arranged; and a plurality of turbulence generators which
are implemented to generate turbulences in the operating liquid to
be evaporated on the evaporator surface; a condenser for condensing
an evaporated operating liquid, which may have a condenser surface
on which an operating liquid is to be arranged; a plurality of
turbulence generators which are implemented to generate current
turbulences in the operating liquid located on the condenser
surface; or a laminarizer which is implemented to make a vapor
current directed to the condenser surface laminar so that a vapor
made laminar by the laminarizer impinges on the operating liquid;
and a compressor for compressing operating liquid evaporated by the
evaporator, wherein the compressor is coupled to the condenser in
order to feed compressed vapor into the condenser, and wherein the
condenser further has a heating forward flow for supplying warm
heating liquid and a heating return flow for supplying cold heating
liquid to the condenser.
[0011] According to another embodiment, method for evaporating an
operating liquid may have the steps of arranging an operating
liquid to be evaporated on an evaporator surface; and generating
turbulences in the operating liquid to be evaporated on the
evaporator surface.
[0012] According to another embodiment, a method for condensing an
evaporated operating liquid may have the steps of arranging
operating liquid on a condenser surface; generating turbulences in
the operating liquid arranged on the condenser surface; or making a
vapor current directed to the condenser surface laminar so that
vapor made laminar hits the operating liquid.
[0013] The present invention is based on the finding that the
evaporation process may be substantially enhanced by the use of
turbulence generators or vortex generators on the evaporator
surface onto which an operating liquid to be evaporated is to be
arranged. The turbulence generators guarantee that no layering
takes place on the operating liquid on the evaporator surface.
Instead, the cold liquid layer forming the surface of the operating
liquid on the evaporating surface is torn apart and brought to the
bottom by the turbulence generators. Simultaneously, the warmer
bottom layer of the operating liquid is brought to the top, so that
it is guaranteed that there is operating liquid at the surface
which has a temperature at which, considering the pressure in the
evaporator which is below the atmospheric pressure and
advantageously even below 50 mbar, an evaporation occurs.
Advantageously, the pressure is selected such that the liquid of
the bottom layer which is turned up to the top by the turbulence
generators is the boiling temperature of the liquid which, as is
known, decreases with decreasing pressure.
[0014] At the condenser side, in one embodiment, the condensation
efficiency is increased by providing turbulence generators also on
the condenser surface, and these turbulence generators lead to a
layering of the liquid on the condenser surface being prevented or
constantly disrupted. Thus, the warmer top layer which absorbed
heat from the condensation process is brought to the bottom and
simultaneously cooler liquid in the condenser is brought to the top
to be heated up by the condensing vapor. In another embodiment, on
the condenser side a laminarization means (means for making
laminar) is present which is implemented to make the vapor stream
directed to the operating liquid laminar. Thus, an advantageous
temperature distribution of the vapor in the laminarization means
is achieved, so that a high condenser efficiency is achieved which
occurs virtually independently of the temperature with which the
vapor enters the condenser space. This is an advantage in
particular with heat pumps with compressors, as typically vapor
overheating exists which normally, without the use of a
laminarizer, leads to a drastic reduction of the condenser
efficiency, which is why vapor coolers are used in conventional
technology. All such measures are no longer needed due to the
laminarizer, as the laminarizer automatically generates a
temperature profile which leads to an optimum efficiency. In one
embodiment both turbulence generators and also a laminarizers are
used on the condenser side, which leads to a further increase of
the condenser efficiency.
[0015] According to a further embodiment, the present invention
relates to an evaporator with an evaporator surface provided with
turbulence generators so that a water stream has turbulences on the
evaporator surface which include at least 20% of the total water
current.
[0016] In a further embodiment, the present invention relates to a
condenser in a condenser space, wherein the condenser space
comprises a laminarizing means to make a gas current directed to a
liquid surface in the condenser laminar, the laminarizer being
implemented to generate a gas stream on the output side which is at
least half as turbulent as a gas stream fed into the laminarizer,
the condenser being provided with turbulence generators so that a
water stream on the condenser surface comprises turbulences
including at least 20% of the total water current.
[0017] Using simplest measures the present invention achieves a
substantial increase of the evaporation efficiency and the
condenser efficiency, wherein this increase may either be used to
manufacture an evaporator or condenser with a higher power.
Alternatively, it is however advantageous to use this substantial
efficiency increase to construct an evaporator and a condenser
substantially smaller and more compact, wherein, however, a certain
performance is achieved. This is a great advantage, in particular
for an application in a heat pump for heating a building for small
and medium-sized buildings, as in buildings, and particularly in
residential buildings, space is typically limited. In addition to
that, a reduction of the size, due to the reduced amount of
material and the easier manageability during manufacturing, leads
to substantial cost savings, which is of special importance
particularly for the use in heat pumps which may be manufactured on
a large scale and have to be of a reasonable price for the
individual clients. At the same time, turbulence generators and
laminarizers may be implemented with the simplest means, thereby
avoiding the use of any electronic/electric elements.
BRIEF DESCRIPTION OF THE DRAWINGS
[0018] In the following, embodiments of the present invention are
explained in more detail with reference to the accompanying
drawings, in which:
[0019] FIG. 1 is a top view onto a condenser or evaporator having
turbulence generators in the form of a simple wire mesh fence.
[0020] FIG. 2 is a honeycomb structure for implementing a
laminarizer in the condenser;
[0021] FIG. 3 is a top view onto a turbulent operating liquid in a
condenser beneath an evaporator;
[0022] FIG. 4a is a schematical illustration of an evaporator with
one embodiment of the present invention;
[0023] FIG. 4b is a schematical illustration of a condenser
according to an embodiment of the present invention;
[0024] FIG. 5 is an overview diagram for illustrating a liquefier
with a gas removal device according to an embodiment of the present
invention;
[0025] FIG. 6a is a plot for illustrating the functionality of the
gas removal device at an inventive condenser;
[0026] FIG. 6b is a detailed illustration of the gas removal
device;
[0027] FIG. 7 is a schematical illustration of a heat pump with an
evaporator according to one embodiment of the present invention
and/or a condenser according to one embodiment of the present
invention;
[0028] FIG. 8a is a top view onto an evaporator or condenser;
[0029] FIG. 8b is a longitudinal section of an evaporator;
[0030] FIG. 9a is a top view onto an evaporator or condenser
according to an alternative embodiment of the present
invention;
[0031] FIG. 9b is a schematical cross-sectional illustration of an
evaporator or condenser according to an embodiment of the present
invention;
[0032] FIG. 10a is a cross-section through a laminarizer according
to an embodiment of the present invention; and
[0033] FIG. 10b is an illustration of the temperature along the
path in a laminarizer cell of the laminarizer.
DETAILED DESCRIPTION OF THE INVENTION
[0034] According to the invention, on the evaporator side and/or on
the condenser side, a means for generating vortexes is provided.
This water vortex generating means which may comprise a plurality
of so-called vortex generators 40, as is illustrated in FIG. 4a and
FIG. 4b, leads to the water current 41 leading to a liquid layer on
a funnel-shaped evaporator 42 or a funnel-shaped condenser 43
passing across the vortex generators. This leads to the water
stream which is to be evaporated or condensed being continuously
subjected to turbulence or vortexes. Thus, the bottom layer of the
water film is continuously mixed with the top layer of the water
film.
[0035] For so-called vortex generators, different materials may be
used, like, for example, a wire mesh fence, as is schematically
illustrated in FIG. 1. This wire mesh fence is arranged in the
water stream or water current so that the wire represents an
obstacle for the water current and continuously leads to a division
of the flow and, so to speak, to a "folding", and thus to a vortex
generation in the water layer.
[0036] The wire mesh illustrated in FIG. 1, which is also known as
"chicken wire", comprises turbulence cells with a diameter of
between 0.5 mm and 3 mm and 1 mm, wherein the distance between
these turbulence cells is approximately one to ten times the
diameter of a turbulence cell or a vortex generator.
[0037] It is to be noted that any other vortex generators may be
used, like, for example, pyramids arranged on the funnel-shaped
evaporator which, so to speak, "cut up" and "fold down" the water
current so that water from the bottom area of the liquid film is
brought to the top and vice versa. It is thus guaranteed that, on
the evaporator side which is plotted in FIG. 4a, "warmer" water is
continuously brought to the evaporator surface and colder water,
i.e. water which has already given off its energy, is mixed
downwards.
[0038] With a heat pump this leads to a substantial power increase.
If an evaporation power of perhaps 1 to 4 kW/m.sup.2, i.e. an
evaporation power per evaporator area, was achieved without a
vortex generator, this evaporation power is substantially
increased, i.e. into a range from 60 to 300 kW/m.sup.2, wherein
already with simple vortex generators, as are, for example,
illustrated in FIG. 1 of the "mesh wire variant", typically 100
kW/m.sup.2 is achieved. The mixing, as is achieved by the vortex
generator 40, thus leads to a destruction of the layering on the
funnel-shaped evaporator, and analog to that also on the
funnel-shaped condenser.
[0039] Although it was noted that the vortex generators may be used
both in the evaporator and also in the condenser, the condenser
power may be increased also without a vortex generator 40 if a gas
current laminarizer 48 is used. Such a gas current or gas stream
laminarizer may, for example, be achieved by a honeycomb-shaped
material in the form of a honeycomb, as is illustrated in FIG. 2.
It has turned out that with a honeycomb cell with a diameter of 3
mm and a honeycomb length of 8 mm already a gas stream
laminarization is achieved, which leads to the gas stream 49, as it
exits the laminarizer 48, being a laminar current. The condenser
efficiency of this laminar current is substantially higher compared
to a situation in which the non-laminarized gas stream hits the
liquid film of the funnel-shaped condenser. The reason for this is
that overheating effects in the gas which is supplied from the
compressor into the condenser, as is illustrated in FIG. 4b, may be
retained.
[0040] Thus, the gradient of the temperature as a function of the
location is very high in the case of a non-laminar current at the
liquid surface. By the inventive laminarization of the gas current,
however, a smaller gradient is achieved directly at the liquid
surface. Thus, the energetic ratios of the gas better suit the
energetic ratios of the liquid, so that the efficiency of the
condensation process is essentially increased.
[0041] The laminarization means is used together with the vortex
generators 40 to achieve an even higher condenser power. However,
also without vortex generators on the condenser side or without a
laminarizer 48 on the condenser side, the efficiency is already
substantially increased.
[0042] According to the invention it is, however, advantageous, on
the condenser side, to use both the vortex generators 40 in the
liquid layer and also the laminarizer 48 for making the current of
the gas laminar. Thus, condenser powers may be achieved which are
up to 100 times higher than condenser powers without vortex
generators and/or laminarizers.
[0043] In FIG. 1, as was already mentioned above, a wire mesh is
illustrated as a vortex generator which is surrounded by water,
which leads to a turbulence generation occurring in the operating
liquid, which does not necessarily have to be water, but which is
advantageously water. This leads to a very even temperature
distribution in the fluid stream flowing off. With a laminar
current, i.e. without the wire mesh as an example of a turbulence
generator, however only a cooling at the surface takes place.
[0044] The honeycomb structure illustrated in FIG. 2 for making the
gas current laminar serves to achieve a smoother temperature
gradient to the fluid surface. Thus, a statistically higher
probability of finding molecules with the suitable energy amount
for condensing at the surface results. If, however, a turbulent gas
stream is used, as is conventionally provided from a compressor and
in particular a turbo compressor, an extremely steep temperature
gradient results and condensing is thus strongly obstructed.
[0045] FIG. 3 shows turbulent water (fluid) on a condenser to
increase the condenser power.
[0046] An arrangement of a device, which is also referred to as a
gas trap 50, in the liquefier 51 of a heat pump is illustrated in
FIG. 5. In particular, FIG. 5 shows a heat pump in which the
liquefier is arranged on top of an evaporator although this
arrangement does not necessarily have to be used to implemented a
gas trap. Water vapor enters a compressor 53 via a first gas
channel 52 and is compressed there and output via a second gas
channel 54. The discharged gas, i.e. the compressed and thus hot
water vapor is advantageously directed to condenser water through
an inventive laminarization means 55 which may, for example, be
implemented in a honeycomb shape or in another way, wherein the
condenser water runs off to the side via a condenser water channel
56 via a plate-shaped or funnel-shaped condenser drain 57. It is to
be noted that the condenser drain 57 is typically rotationally
symmetric and provided with an inventive turbulence generator 58 to
increase the condenser efficiency.
[0047] Foreign gases sucked in by the compressor motor 53 from the
evaporator are directed, due to the gas current through the
laminarizer 55, to the condenser water 56, which runs off to the
side coming from the center over the turbulence generator 58 which
may, for example, be implemented in the form of a wire mesh. It has
turned out that foreign gases are carried off to the side by the
condenser water between the laminarizer 55 and the condenser water
surface.
[0048] For the foreign gases to accumulate in the proximity of the
gas trap 50, a sealing lip 59 is provided which separates the
bottom gas area 60 from the top gas area 61. Thus, the sealing lip
59 does not necessarily have to provide a complete sealing. It
guarantees, however, that the foreign gas transported by the
condenser water on the condenser 57 accumulates below the condenser
drain 57 in the area 60. Foreign gases, as they are heavier than
water vapor, fall into the gas trap 50 due to gravity. A diffusion
process acts against gravity, insofar as also the foreign gases
want to have the same concentration in the area 60 and in the gas
trap. This diffusion process thus acts against the gravity effect
of the gas trap. This is relatively unproblematic, however, as the
accumulation of the foreign gas now no longer takes place in the
area where condensation takes place, but below the drain 57. By the
sealing lip 59, it is prevented that the concentrations in the area
60 and in the area 61 are set to the same value. Thus, the
concentration of the foreign gas in the space 60 will be higher
than in the space 61, and a good trapping effect for foreign gases
will occur in the gas trap 50.
[0049] The effect of the sealing lip 59, which separates the area
above the condenser drain or the condenser funnel 57 from the area
below this element 57, is increased by the fact that the
laminarization means 55 is present, as thus the foreign gases, as
soon as they meet the water current 56 on the liquefier drain 57,
may not leave again, but are forced, so to speak, to pass in the
direction of the sealing lip and below the sealing lip to
accumulate in the proximity of the gas trap 50. This performance is
even increased by the turbulence generator 58 as then a more
turbulent current exists which also has a higher efficiency, so to
speak, to trap and carry foreign gas which is in the top area
61.
[0050] FIG. 6a shows a basic illustration of the functionality
which was illustrated in respect of the heat pump or the heat pump
liquefier 51 of FIG. 5. In FIG. 6a it is particularly emphasized
how the space 260 below the drain 57 is separated from the top area
61 by the sealing lip 59. This separation, as is clearly obvious in
FIG. 6a, does not have to be hermetic as long as a higher
probability exists that foreign gases follow the turbulent water
vapor, which was, however, laminarized by the laminarizer 55, as is
illustrated by arrows 69, on the path into the lower area 60, as is
indicated by an arrow 68, with a higher probability in comparison
to the probability that the foreign gases again enter the top area
61. Thus, in the area 60 an accumulation of foreign gases will take
place, so that the diffusion effect is, so to speak, reduced from
the gas trap 50 and the efficiency of the gas trap is not
substantially affected.
[0051] It is advantageous, depending on the implementation, to
implement the gas trap similar to FIG. 6b. For this purpose, the
gas trap has a relatively long neck 70 which extends between the
accumulation container 71 and an existing inlet area 72 which may
be funnel-shaped. However, it is not the length of the neck 70 that
is important, but that at least the bottom part of the accumulation
container 10 is arranged in a cold area, like, for example, the
evaporator 2 of the heat pump. This means that warm water vapor
from the area 60 of the liquefier comes into contact with a cold
surface of the accumulation container 1, which leads to a
condensation of the water vapor. Thus, a continuous water vapor
current into the funnel 72 along the neck 70 into the accumulation
container results, as the water vapor in the area 50 condenses at
the cold wall of the accumulation container arranged in the
evaporator 2. The thus resulting current into the gas trap serves,
on the one hand, to carry also foreign gases into the accumulation
container and at the same time serves to accumulate water in the
accumulation container which may then be heated up by the pressure
generating means 1 in the form of a heating coil to cause the vapor
output. Also at the funnel opening, a laminarization means 73 is
arranged, like, for example, in the form of a honeycomb-shaped
structure in order to improve the efficiency of the gas trap.
[0052] The implementation of arranging a wall of the accumulation
container 10 in the evaporator, or, generally speaking, at a cold
location of the system, is especially advantageous when the heat
pump is implemented such that the liquefier is arranged above the
evaporator. In this implementation, the neck 70 reaches through the
liquefier downwards into the evaporator to provide a cold
condensation wall which, on the one hand, leads to a continuous gas
stream into the gas trap and, on the other hand, causes water to be
present in the gas trap, which may be heated to increase the
pressure in the accumulation container such that at certain events
a discharge of foreign gas may take place.
[0053] FIG. 7 shows a schematical illustration of a heat pump for
heating a building. The heat pump for heating a building is
implemented such that detached houses or small apartment houses may
be heated. The heat pump for heating buildings according to one
embodiment of the present invention is to be implemented to heat
small apartment houses with less than 10 apartments and
advantageously less that 5 apartments. The heat pump includes an
evaporator with an evaporator housing 42' with turbulence
generators. The vapor generated in the evaporator is supplied via a
vapor line 100 to a compressor 102. The compressor 102 compresses
the vapor and leads the compressed vapor via a vapor line for
compressed vapor, designated by 104, into an inventive condenser
having a condenser housing 43' which comprises either turbulence
generators or a laminarizer or advantageously both means to acquire
a more efficient condensation. The evaporator receives the liquid
to be evaporated via a supply line 106 and the condenser discharges
the condensed liquid via a discharge line 108. In addition to that,
the condenser 43 comprises a forward flow 110a with temperatures,
for example, in a range of 40.degree. for floor heating and a
return flow 110b from the heating system of the building. In the
radiator, such as, for example, the floor heating or a wall heating
element, the same liquid may flow as in the condenser without a
heat exchanger being provided. Alternatively, however, also a heat
exchanger may be provided so that the forward flow 110a and the
return flow 100b lead to a heat exchanger not illustrated in FIG. 7
and not into an actual radiator. The discharge line 108, in the
case of an open system, may lead into an open water reservoir,
like, for example, ground water, sea water, saline water, river
water, etc. Likewise, in such an open system the supply line 106
may come from underground water, sea water, river water, saline
water, etc. Alternatively, also a closed system may be used, as is
indicated by the dashed connecting lines to a connecting element
110. In this case, the connecting element 110 guarantees that the
liquid condensed in the condenser is again supplied into the
evaporator, wherein corresponding pressure differences are
considered.
[0054] It is further to be noted that, in the case of a half-open
system, although the liquid 106 in the supply line carries heat
from the underground water, it is not underground water, wherein in
this case a heat exchanger is arranged in an underground water
reservoir to heat up the circulating liquid in the line 106, which
is then implemented as a go and return line so that the heat
transmitted by the underground water is brought into the heating
forward flow 110a via the heat pump process.
[0055] In an embodiment of the present invention, the operating
liquid in the evaporator and in the condenser is water.
Alternatively, however, also other operating liquids may be used,
like, for example, heat-carrier liquids provided especially for
heat pumps. Water is, however, advantageous due to its special
suitability for the process. A further substantial advantage of
water is that it is carbon neutral.
[0056] To evaporate water at temperatures of approximately
10.degree. C., the evaporator 42 is provided with an evaporator
housing which is implemented to maintain a pressure in the
evaporator at least in the environment of the evaporator surface at
which the water flowing in the supply line 106 evaporates. If water
is used as the operating liquid, pressures in the evaporator will
be below 30 mbar and even in a range below 10 mbar.
[0057] On the condenser side, pressures will be at more than 40
mbar and below 200 or 150 mbar. In this respect, a condenser
housing is implemented to maintain the respective pressures.
Pressures at condensation temperatures of 30.degree. C. or below or
22.degree. C. or below are advantageous.
[0058] FIG. 8A shows a top view onto an evaporator or condenser
with wire sections as turbulence generators, and FIG. 8B shows a
longitudinal section of the evaporator, which, analogous to this,
may also be the condenser if corresponding forward/return lines,
etc. are considered and the condenser liquid is not externally
supplied and drained but circulates.
[0059] The evaporator includes an evaporator surface or condenser
surface 80 arranged on the turbulence generators 40. The turbulence
generators 40 are individual wire sections, together implemented,
for example, as a spiral 82. Simultaneously, the turbulence
generators may also be more or less concentric wire rings separate
from each other, but the use of a spiral is easier with regard to
handling and assembly. In the flow direction of the operating
liquid, indicated with the symbolic arrows 83, adjacent wire
sections 84a, 84b which each have a diameter of d are spaced apart
by a distance D.sub.d, wherein the distance D.sub.d is greater than
the diameter d of a wire section and advantageously smaller than
three times the diameter. Although the wire sections in FIG. 8A are
plotted having a circular cross-section, the cross-section of the
wire sections is arbitrary.
[0060] In the longitudinal section, FIG. 8B shows a funnel-shaped
evaporator or condenser or a funnel-shaped evaporator surface or
condenser surface 80. The wire sections are mounted directly on
this surface 80. Alternatively, the wire sections may also be
spaced apart, as long as a relative positioning of the turbulence
generators 40 with respect to the surface 80 is provided which is
such that it acts upon the operating liquid present on the surface
80 by means of the turbulence generators, so that turbulences
result.
[0061] The surface 80, both for the evaporator and also for the
condenser, is shaped such that the operating liquid which is
supplied via an operating liquid supply line 86 not only stands
still on the surface 80, which would be the case if the surface
were completely horizontal and a virtually non-existing supply line
were present, but that the operating liquid also flows on the
surface due to gravity. For this purpose, the surface 80 includes
at least one inclined plane. Advantageously, the surface is
funnel-shaped and the supply opening 86 is in the center or
arranged with respect to the operating surface such that the
operating liquid is not only drained at one side with respect to
the supply opening, but flows off to all sides. Alternatively,
however, also an implementation for certain applications may be
used, in which, for example, a level area exists which is arranged
as an inclined plane and where, at the highest point, the intake or
supply line 86 is arranged so that the operating liquid is not on
several sides of the intake but basically in a limited sector,
like, for example, 30.degree., 60.degree. or 90.degree. with
respect to the intake on the surface, in order to cause an effect
there by the turbulence generators 40.
[0062] Alternatively, the operating surface may also be
pyramid-shaped or conical or uneven or curved in its cross-section
as long as the operating liquid, in the operating position of the
evaporator or condenser, overcomes a height difference due to the
effect of gravity.
[0063] FIGS. 9A and 9B show a top view onto an alternative surface
80 of an evaporator or condenser, wherein no wire sections as in
FIG. 8A exist but elevations or indentations exist in the operating
surface. In FIG. 9B, only elevations are illustrated. The
indentations will be implemented similarly but, so to speak,
"negatively" with respect to the illustrated elevations. The
turbulence generators 40 protrude from the surface or are set back
from the surface, i.e. practically as "holes" in the surface 80,
wherein the turbulence generators 40 protrude so far over the
surface that they protrude, at least with their tip, beyond a level
of the operating liquid 41 on the surface 80. Further, the
turbulence generators 40 may have any shape, as indicated in FIG.
9B. The more abrupt the shapes are, the more "whirls" or
turbulences are generated. Simultaneously, the turbulence
generators may also be implemented to achieve, using special forms,
a "separation" and "folding" of the water current.
[0064] Apart from the illustrated implementations, the turbulence
generators may, for example, also be implemented by elements
reaching into the operating liquid, like, for example, bars, etc.
which are not firmly connected to the surface 80 but are suspended
above the surface 80, for example. These bars may also be moved,
depending on the implementation, to generate extremely strong
turbulences. Turbulences may thus be generated in many ways,
wherein turbulence generators, in order to generate these
turbulences, may be firmly connected with the operating surface 80
or also be positioned in a static or dynamic way with respect to
the operating surface as long as, advantageously, at least 20% of
the overall water current is provided with turbulences. It is
advantageous in special embodiments to provide almost the complete
operating surface of the evaporator or condenser with turbulence
generators as far as possible, so that between 90% and almost 100%
of the complete current is turbulent or, with respect to the area
of the surface 80, more than 80% or more than 90% of the liquid on
the surface 80 is in turbulence.
[0065] FIG. 10A shows a cross-section through a laminarizing means
having different laminarizing cells 120. Above the laminarizing
cells 120, turbulent vapor with a temperature .theta..sub.D exists,
as is schematically indicated by the undirected vapor arrows 122.
Below the laminarizer cells 120, however, vapor 122 made laminar is
illustrated which, due to the fact that it is close to the liquid
of the condenser on the condenser surface 80, has a temperature of
about .theta..sub.w. .theta..sub.w is lower than .theta..sub.D. The
course of the temperature in a laminarizer cell of x=0 to x=L is
schematically illustrated in FIG. 10B. An exponential connection
may be seen, wherein the temperature at x=0 is approximately
.theta..sub.w and via an approximately exponential connection
reaches the temperature .theta..sub.D at x=L. This connection is
characterized by a position constant K indicated in FIG. 10B. For a
good laminarization and thus a good temperature distribution to
take place, it is advantageous to implement the length of a
laminarizer cell 120 to be at least so large that the length is
greater or equal 2K.
[0066] In addition to that, with the present invention the
temperature of the undirected vapor .theta..sub.D may be far higher
than the temperature of the water .theta..sub.w. Still, no vapor
coolers, etc. are needed, as the laminarizer 48 with the individual
laminarizer cells 120 separated from each other by walls 121
enforces the temperature distribution illustrated in FIG. 10b. In
the embodiment, the laminarizer is honeycomb-shaped or made of a
tube material, as long as individual laminarizer cells 120 exist
which are directed in a more or less parallel way and are smooth on
the inside and which cause a laminarization as is illustrated by
the directed vapor current 124.
[0067] The laminarizer does not necessarily have to achieve a
perfect 100% laminarization as long as the gas current at the
output of the laminarizer is less turbulent than the gas stream at
the input of the laminarizer. Advantageously, the laminarizer cells
or the whole laminarizer is implemented so that the output vapor
current made laminar is at least half as turbulent as the turbulent
vapor current on the input side.
[0068] For use in a condenser for a heat pump operated with water
as the operating liquid, it is advantageous for the length of a
laminarizer cell 120 to be approximately 10 mm long if the diameter
of the laminarizer cell is 5 mm. The larger the diameter of an
individual cell, the longer also the length L ought to be, so that
also with larger diameters a sufficient laminarization is achieved.
At the same time, with smaller diameters there is a lower limit of
the length in order to prevent a nozzle effect occurring which may
lead to a de-laminarization. To keep the flow resistance for the
vapor as low as possible, it is advantageous to provide a large
laminarizer area and to implement the thickness of the walls 121
between the laminarizer cells 120 in FIG. 10A as low as possible.
Advantageously, if the diameter is smaller than 1 mm, the length is
longer than 1 mm. Other favorable exemplary dimension are: if the
diameter is greater than 5 mm, the length is greater than 10 mm,
and if the diameter is smaller than 5 mm, the length is smaller
than 10 mm.
[0069] In order to guarantee, also with incomplete laminarization,
that a basically laminarized current meets the liquid on the
condenser surface, it is advantageous to implement the distance
D.sub.L between the output of the laminarizer cells 120 and the
surface of the liquid to be relatively small and in particular
smaller than 50 mm, advantageously smaller than 25 mm or
advantageously smaller than 6 mm. It is thus also enforced that the
gas or the evaporated operating liquid when it leaves the
laminarizer cells has a temperature which is virtually equal to or
only slightly higher than the temperature of the water. It is thus
guaranteed that the vapor particles in the current do not "bounce
off" the water or again act as vapor generators but are integrated
into the water by condensation, as only in this way an especially
efficient heat transmission from vapor to water may take place.
[0070] The inventive laminarizer provides a substantial increase of
the efficiency when condensing. In conventional technology without
laminarizers, the efficiency of power per area strongly decreased
the higher the temperature of the vapor with respect to the
temperature of the condenser liquid. It may thus be said that, when
overheating the vapor by 10.degree., only 10% of the condenser
power was possible. This consequently led to condenser powers of
2-3 kW per m.sup.2 for a typical surface condensation or
evaporation. According to the invention, with the same area a
substantially higher power is achieved depending on the
implementation of 40-200 kW/m.sup.2 or even more. This means
increasing the efficiency by a factor of 20 with simple means. A
further advantage is that the efficiency is relatively independent
of the temperature of the undirected vapor. It is thus easily
possible according to the invention to condense vapor with a
temperature of, for example, more than 150.degree. C. with water
which is, for example, at 40.degree. C. The laminarizer thus
provides a decoupling of the condenser efficiency from the vapor
temperature at the output of the compressor. Thus, the compressor
may be dimensioned according to its requirements, and it does not
have to be considered in the dimensioning of the compressor
according to the present invention which thermal conditions are
needed for condensing.
[0071] Deviating from the above-described embodiments, the
turbulence generators and the laminarizing means may not be
implemented as two separate elements but also as one and the same
element. For example, a fiber tissue or a fiber mat advantageously
made of non-absorbent fibers may be placed onto the evaporator
surface or the condenser surface, wherein the surface of the fiber
tissue protrudes from the level of the liquid, advantageously by
more than 3 mm and in particular by more than 5 mm. The liquid
flows around the fibers, whereby turbulences are generated. The
washed-around fibers represent the turbulence generators. The
fibers protruding from the liquid which are not washed-around do,
however, represent the laminarization means. The friction of the
vapor at the fibers, which do not necessarily have to be directed,
leads to a laminarization of the vapor. The material of the fibers
is plastic or metal, and the fiber tissue is, for example, metallic
wool or, in particular, steel wool. An advantage of this
implementation is that this implementation is self-adjusting, as
the separation into turbulence generator and laminarization means
is automatic and is defined by the current liquid level. Apart from
that, the assembly is especially simple and thus
cost-effective.
[0072] Although certain elements have been described as device
features, at the same time this should represent a description of
the corresponding method step.
[0073] While this invention has been described in terms of several
embodiments, there are alterations, permutations, and equivalents
which fall within the scope of this invention. It should also be
noted that there are many alternative ways of implementing the
methods and compositions of the present invention. It is therefore
intended that the following appended claims be interpreted as
including all such alterations, permutations and equivalents as
fall within the true spirit and scope of the present invention.
* * * * *