BACKGROUND
[0001] The application relates generally to vapor compression systems in refrigeration,
air conditioning and chilled liquid systems. The application relates more specifically
to distribution systems and methods in vapor compression systems.
[0002] Conventional chilled liquid systems used in heating, ventilation and air conditioning
systems include an evaporator to effect a transfer of thermal energy between the refrigerant
of the system and another liquid to be cooled. One type of evaporator includes a shell
with a plurality of tubes forming a tube bundle(s) through which the liquid to be
cooled is circulated. The refrigerant is brought into contact with the outer or exterior
surfaces of the tube bundle inside the shell, resulting in a transfer of thermal energy
between the liquid to be cooled and the refrigerant. For example, refrigerant can
be deposited onto the exterior surfaces of the tube bundle by spraying or other similar
techniques in what is commonly referred to as a "falling film" evaporator. Illustrative
refrigerant distributions systems for use in evaporators are known from
CA 1 064 815 A1,
US 1 944 056 and
US 1 732 963 A. In a further example, the exterior surfaces of the tube bundle can be fully or partially
immersed in liquid refrigerant in what is commonly referred to as a "flooded" evaporator.
In yet another example, a portion of the tube bundle can have refrigerant deposited
on the exterior surfaces and another portion of the tube bundle can be immersed in
liquid refrigerant in what is commonly referred to as a "hybrid falling film" evaporator.
[0003] As a result of the thermal energy transfer with the liquid, the refrigerant is heated
and converted to a vapor state, which is then returned to a compressor where the vapor
is compressed, to begin another refrigerant cycle. The cooled liquid can be circulated
to a plurality of heat exchangers located throughout a building. Warmer air from the
building is passed over the heat exchangers where the cooled liquid is warmed, while
cooling the air for the building. The liquid warmed by the building air is returned
to the evaporator to repeat the process.
SUMMARY
[0004] The present invention is defined by the independent claims. The dependent claims
define advantageous embodiments.
BRIEF DESCRIPTION OF THE FIGURES
[0005]
FIG. 1 shows an exemplary embodiment for a heating, ventilation and air conditioning
system.
FIG. 2 shows an isometric view of an exemplary vapor compression system.
FIGS. 3 and 4 schematically illustrate exemplary embodiments of the vapor compression
system.
FIG. 5A shows an exploded, partial cutaway view of an exemplary evaporator.
FIG. 5B shows a top isometric view of the evaporator of FIG. 5A.
FIG. 5C shows a cross section of the evaporator taken along line 5-5 of FIG. 5B.
FIG. 6A shows a top isometric view of an exemplary evaporator.
FIGS. 6B and 6C show a cross section of the evaporator taken along line 6-6 of FIG.
6A.
FIG. 7 shows an upper perspective of an exemplary embodiment of an enclosure.
FIG. 8 shows a plan view of the enclosure of FIG. 7.
FIG. 9 shows a partial front view of the enclosure taken along line 9-9 of FIG. 7.
FIG. 10 shows a cross section of the enclosure taken along line 10-10 of FIG. 9.
FIG. 11 shows a cross section of an exemplary embodiment of the enclosure taken along
line 10-10 of FIG. 9.
FIG. 12 shows a cross section of a further exemplary embodiment of the enclosure taken
along line 10-10 of FIG. 9.
FIG. 13 shows a cross section of a further exemplary embodiment of the enclosure taken
along line 10-10 of FIG. 9.
FIG. 14 shows a cross section of yet a further exemplary embodiment of the enclosure
taken along line 10-10 of FIG. 9.
FIG. 15 shows an exemplary embodiment of the enclosure.
DETAILED DESCRIPTION OF THE EXEMPLARY EMBODIMENTS
[0006] FIG. 1 shows an exemplary environment for a heating, ventilation and air conditioning
(HVAC) system 10 incorporating a chilled liquid system in a building 12 for a typical
commercial setting. System 10 can include a vapor compression system 14 that can supply
a chilled liquid which may be used to cool building 12. System 10 can include a boiler
16 to supply heated liquid that may be used to heat building 12, and an air distribution
system which circulates air through building 12. The air distribution system can also
include an air return duct 18, an air supply duct 20 and an air handler 22. Air handler
22 can include a heat exchanger that is connected to boiler 16 and vapor compression
system 14 by conduits 24. The heat exchanger in air handler 22 may receive either
heated liquid from boiler 16 or chilled liquid from vapor compression system 14, depending
on the mode of operation of system 10. System 10 is shown with a separate air handler
on each floor of building 12, but it is appreciated that the components may be shared
between or among floors.
[0007] FIGS. 2 and 3 show an exemplary vapor compression system 14 that can be used in an
HVAC system, such as HVAC system 10. Vapor compression system 14 can circulate a refrigerant
through a compressor 32 driven by a motor 50, a condenser 34, expansion device(s)
36, and a liquid chiller or evaporator 38. Vapor compression system 14 can also include
a control panel 40 that can include an analog to digital (A/D) converter 42, a microprocessor
44, a non-volatile memory 46, and an interface board 48. Some examples of fluids that
may be used as refrigerants in vapor compression system 14 are hydrofluorocarbon (HFC)
based refrigerants, for example, R-410A, R-407, R-134a, hydrofluoro olefin (HFO),
"natural" refrigerants like ammonia (NH3), R-717, carbon dioxide (CO2), R-744, or
hydrocarbon based refrigerants, water vapor or any other suitable type of refrigerant.
In an exemplary embodiment, vapor compression system 14 may use one or more of each
of VSDs 52, motors 50, compressors 32, condensers 34 and/or evaporators 38.
[0008] Motor 50 used with compressor 32 can be powered by a variable speed drive (VSD) 52
or can be powered directly from an alternating current (AC) or direct current (DC)
power source. VSD 52, if used, receives AC power having a particular fixed line voltage
and fixed line frequency from the AC power source and provides power having a variable
voltage and frequency to motor 50. Motor 50 can include any type of electric motor
that can be powered by a VSD or directly from an AC or DC power source. For example,
motor 50 can be a switched reluctance motor, an induction motor, an electronically
commutated permanent magnet motor or any other suitable motor type. In an alternate
exemplary embodiment, other drive mechanisms such as steam or gas turbines or engines
and associated components can be used to drive compressor 32.
[0009] Compressor 32 compresses a refrigerant vapor and delivers the vapor to condenser
34 through a discharge line. Compressor 32 can be a centrifugal compressor, screw
compressor, reciprocating compressor, rotary compressor, swing link compressor, scroll
compressor, turbine compressor, or any other suitable compressor. The refrigerant
vapor delivered by compressor 32 to condenser 34 transfers heat to a fluid, for example,
water or air. The refrigerant vapor condenses to a refrigerant liquid in condenser
34 as a result of the heat transfer with the fluid. The liquid refrigerant from condenser
34 flows through expansion device 36 to evaporator 38. In the exemplary embodiment
shown in FIG. 3, condenser 34 is water cooled and includes a tube bundle 54 connected
to a cooling tower 56.
[0010] The liquid refrigerant delivered to evaporator 38 absorbs heat from another fluid,
which may or may not be the same type of fluid used for condenser 34, and undergoes
a phase change to a refrigerant vapor. In the exemplary embodiment shown in FIG. 3,
evaporator 38 includes a tube bundle having a supply line 60S and a return line 60R
connected to a cooling load 62. A process fluid, for example, water, ethylene glycol,
calcium chloride brine, sodium chloride brine, or any other suitable liquid, enters
evaporator 38 via return line 60R and exits evaporator 38 via supply line 60S. Evaporator
38 chills the temperature of the process fluid in the tubes. The tube bundle in evaporator
38 can include a plurality of tubes and a plurality of tube bundles. The vapor refrigerant
exits evaporator 38 and returns to compressor 32 by a suction line to complete the
cycle.
[0011] FIG. 4, which is similar to FIG. 3, shows the refrigerant circuit with an intermediate
circuit 64 that may be incorporated between condenser 34 and expansion device 36 to
provide increased cooling capacity, efficiency and performance. Intermediate circuit
64 has an inlet line 68 that can be either connected directly to or can be in fluid
communication with condenser 34. As shown, inlet line 68 includes an expansion device
66 positioned upstream of an intermediate vessel 70. Intermediate vessel 70 can be
a flash tank, also referred to as a flash intercooler, in an exemplary embodiment.
In an alternate exemplary embodiment, intermediate vessel 70 can be configured as
a heat exchanger or a "surface economizer." In the flash intercooler arrangement,
a first expansion device 66 operates to lower the pressure of the liquid received
from condenser 34. During the expansion process in a flash intercooler, a portion
of the liquid is evaporated. Intermediate vessel 70 may be used to separate the evaporated
vapor from the liquid received from the condenser. The evaporated liquid may be drawn
by compressor 32 to a port at a pressure intermediate between suction and discharge
or at an intermediate stage of compression, through a line 74. The liquid that is
not evaporated is cooled by the expansion process, and collects at the bottom of intermediate
vessel 70, where the liquid is recovered to flow to the evaporator 38, through a line
72 comprising a second expansion device 36.
[0012] In the "surface intercooler" arrangement, the implementation is slightly different,
as known to those skilled in the art. Intermediate circuit 64 can operate in a similar
matter to that described above, except that instead of receiving the entire amount
of refrigerant from condenser 34, as shown in FIG. 4, intermediate circuit 64 receives
only a portion of the refrigerant from condenser 34 and the remaining refrigerant
proceeds directly to expansion device 36.
[0013] FIGS. 5A-5C show an exemplary embodiment of an evaporator configured as a "hybrid
falling film" evaporator. As shown in FIGS. 5A-5C, an evaporator 138 includes a substantially
cylindrical shell 76 with a plurality of tubes forming a tube bundle 78 extending
substantially horizontally along the length of shell 76. At least one support 116
may be positioned inside shell 76 to support the plurality of tubes in tube bundle
78. A suitable fluid, such as water, ethylene, ethylene glycol, or calcium chloride
brine flows through the tubes of tube bundle 78. A distributor 80 positioned above
tube bundle 78 distributes, deposits or applies refrigerant 110 from a plurality of
positions onto the tubes in tube bundle 78. In one exemplary embodiment, the refrigerant
deposited by distributor 80 can be entirely liquid refrigerant, although in another
exemplary embodiment, the refrigerant deposited by distributor 80 can include both
liquid refrigerant and vapor refrigerant.
[0014] Liquid refrigerant that flows around the tubes of tube bundle 78 without changing
state collects in the lower portion of shell 76. The collected liquid refrigerant
can form a pool or reservoir of liquid refrigerant 82. The deposition positions from
distributor 80 can include any combination of longitudinal or lateral positions with
respect to tube bundle 78. In another exemplary embodiment, deposition positions from
distributor 80 are not limited to ones that deposit onto the upper tubes of tube bundle
78. Distributor 80 may include a plurality of nozzles supplied by a dispersion source
of the refrigerant. In an exemplary embodiment, the dispersion source is a tube connecting
a source of refrigerant, such as condenser 34. Nozzles include spraying nozzles, but
also include machined openings that can guide or direct refrigerant onto the surfaces
of the tubes. The nozzles may apply refrigerant in a predetermined pattern, such as
a jet pattern, so that the upper row of tubes of tube bundle 78 are covered. The tubes
of tube bundle 78 can be arranged to promote the flow of refrigerant in the form of
a film around the tube surfaces, the liquid refrigerant coalescing to form droplets
or in some instances, a curtain or sheet of liquid refrigerant at the bottom of the
tube surfaces. The resulting sheeting promotes wetting of the tube surfaces which
enhances the heat transfer efficiency between the fluid flowing inside the tubes of
tube bundle 78 and the refrigerant flowing around the surfaces of the tubes of tube
bundle 78.
[0015] In the pool of liquid refrigerant 82, a tube bundle 140 can be immersed or at least
partially immersed, to provide additional thermal energy transfer between the refrigerant
and the process fluid to evaporate the pool of liquid refrigerant 82. In an exemplary
embodiment, tube bundle 78 can be positioned at least partially above (that is, at
least partially overlying) tube bundle 140. In one exemplary embodiment, evaporator
138 incorporates a two pass system, in which the process fluid that is to be cooled
first flows inside the tubes of tube bundle 140 and then is directed to flow inside
the tubes of tube bundle 78 in the opposite direction to the flow in tube bundle 140.
In the second pass of the two pass system, the temperature of the fluid flowing in
tube bundle 78 is reduced, thus requiring a lesser amount of heat transfer with the
refrigerant flowing over the surfaces of tube bundle 78 to obtain a desired temperature
of the process fluid.
[0016] It is to be understood that although a two pass system is described in which the
first pass is associated with tube bundle 140 and the second pass is associated with
tube bundle 78, other arrangements are contemplated. For example, evaporator 138 can
incorporate a one pass system where the process fluid flows through both tube bundle
140 and tube bundle 78 in the same direction. Alternatively, evaporator 138 can incorporate
a three pass system in which two passes are associated with tube bundle 140 and the
remaining pass associated with tube bundle 78, or in which one pass is associated
with tube bundle 140 and the remaining two passes are associated with tube bundle
78. Further, evaporator 138 can incorporate an alternate two pass system in which
one pass is associated with both tube bundle 78 and tube bundle 140, and the second
pass is associated with both tube bundle 78 and tube bundle 140. In one exemplary
embodiment, tube bundle 78 is positioned at least partially above tube bundle 140,
with a gap separating tube bundle 78 from tube bundle 140. In a further exemplary
embodiment, hood 86 overlies tube bundle 78, with hood 86 extending toward and terminating
near the gap. In summary, any number of passes in which each pass can be associated
with one or both of tube bundle 78 and tube bundle 140 is contemplated.
[0017] An enclosure or hood 86 is positioned over tube bundle 78 to substantially prevent
cross flow, that is, a lateral flow of vapor refrigerant or liquid and vapor refrigerant
106 between the tubes of tube bundle 78. Hood 86 is positioned over and laterally
borders tubes of tube bundle 78. Hood 86 includes an upper end 88 positioned near
the upper portion of shell 76. Distributor 80 can be positioned between hood 86 and
tube bundle 78. In yet a further exemplary embodiment, distributor 80 may be positioned
near, but exterior of, hood 86, so that distributor 80 is not positioned between hood
86 and tube bundle 78. However, even though distributor 80 is not positioned between
hood 86 and tube bundle 78, the nozzles of distributor 80 are still configured to
direct or apply refrigerant onto surfaces of the tubes. Upper end 88 of hood 86 is
configured to substantially prevent the flow of applied refrigerant 110 and partially
evaporated refrigerant, that is, liquid and/or vapor refrigerant 106 from flowing
directly to outlet 104. Instead, applied refrigerant 110 and refrigerant 106 are constrained
by hood 86, and, more specifically, are forced to travel downward between walls 92
before the refrigerant can exit through an open end 94 in the hood 86. Flow of vapor
refrigerant 96 around hood 86 also includes evaporated refrigerant flowing away from
the pool of liquid refrigerant 82.
[0018] It is to be understood that at least the above-identified, relative terms are nonlimiting
as to other exemplary embodiments in the disclosure. For example, hood 86 may be rotated
with respect to the other evaporator components previously discussed, that is, hood
86, including walls 92, is not limited to a vertical orientation. Upon sufficient
rotation of hood 86 about an axis substantially parallel to the tubes of tube bundle
78, hood 86 may no longer be considered "positioned over" nor to "laterally border"
tubes of tube bundle 78. Similarly, "upper" end 88 of hood 86 may no longer be near
"an upper portion" of shell 76, and other exemplary embodiments are not limited to
such an arrangement between the hood and the shell. In an exemplary embodiment, hood
86 terminates after covering tube bundle 78, although in another exemplary embodiment,
hood 86 further extends after covering tube bundle 78.
[0019] After hood 86 forces refrigerant 106 downward between walls 92 and through open end
94, the vapor refrigerant undergoes an abrupt change in direction before traveling
in the space between shell 76 and walls 92 from the lower portion of shell 76 to the
upper portion of shell 76. Combined with the effect of gravity, the abrupt directional
change in flow results in a proportion of any entrained droplets of refrigerant colliding
with either liquid refrigerant 82 or shell 76, thereby removing those droplets from
the flow of vapor refrigerant 96. Also, refrigerant mist traveling along the length
of hood 86 between walls 92 is coalesced into larger drops that are more easily separated
by gravity, or maintained sufficiently near or in contact with tube bundle 78, to
permit evaporation of the refrigerant mist by heat transfer with the tube bundle.
As a result of the increased drop size, the efficiency of liquid separation by gravity
is improved, permitting an increased upward velocity of vapor refrigerant 96 flowing
through the evaporator in the space between walls 92 and shell 76. Vapor refrigerant
96, whether flowing from open end 94 or from the pool of liquid refrigerant 82, flows
over a pair of extensions 98 protruding from walls 92 near upper end 88 and into a
channel 100. Vapor refrigerant 96 enters into channel 100 through slots 102, which
is the space between the ends of extensions 98 and shell 76, before exiting evaporator
138 at an outlet 104. In another exemplary embodiment, vapor refrigerant 96 can enter
into channel 100 through openings or apertures formed in extensions 98, instead of
slots 102. In yet another exemplary embodiment, slots 102 can be formed by the space
between hood 86 and shell 76, that is, hood 86 does not include extensions 98.
[0020] Stated another way, once refrigerant 106 exits from hood 86, vapor refrigerant 96
then flows from the lower portion of shell 76 to the upper portion of shell 76 along
the prescribed passageway. In an exemplary embodiment, the passageways can be substantially
symmetric between the surfaces of hood 86 and shell 76 prior to reaching outlet 104.
In an exemplary embodiment, baffles, such as extensions 98 are provided near the evaporator
outlet to prevent a direct path of vapor refrigerant 96 to the compressor inlet.
[0021] In one exemplary embodiment, hood 86 includes opposed substantially parallel walls
92. In another exemplary embodiment, walls 92 can extend substantially vertically
and terminate at open end 94, that is located substantially opposite upper end 88.
Upper end 88 and walls 92 are closely positioned near the tubes of tube bundle 78,
with walls 92 extending toward the lower portion of shell 76 so as to substantially
laterally border the tubes of tube bundle 78. In an exemplary embodiment, walls 92
may be spaced between about 0.02 inch (0.5 mm) and about 0.8 inch (20 mm) from the
tubes in tube bundle 78. In a further exemplary embodiment, walls 92 may be spaced
between about 0.1 inch (3 mm) and about 0.2 inch (5 mm) from the tubes in tube bundle
78. However, spacing between upper end 88 and the tubes of tube bundle 78 may be significantly
greater than 0.2 inch (5 mm), in order to provide sufficient spacing to position distributor
80 between the tubes and the upper end of the hood. In an exemplary embodiment in
which walls 92 of hood 86 are substantially parallel and shell 76 is cylindrical,
walls 92 may also be symmetric about a central vertical plane of symmetry of the shell
bisecting the space separating walls 92. In other exemplary embodiments, walls 92
need not extend vertically past the lower tubes of tube bundle 78, nor do walls 92
need to be planar, as walls 92 may be curved or have other nonplanar shapes. Regardless
of the specific construction, hood 86 is configured to channel refrigerant 106 within
the confines of walls 92 through open end 94 of hood 86.
[0022] FIGS. 6A-6C show an exemplary embodiment of an evaporator configured as a "falling
film" evaporator 128. As shown in FIGS. 6A-6C, evaporator 128 is similar to evaporator
138 shown in FIGS. 5A-5C, except that evaporator 128 does not include tube bundle
140 in the pool of refrigerant 82 that collects in the lower portion of the shell.
In an exemplary embodiment, hood 86 terminates after covering tube bundle 78, although
in another exemplary embodiment, hood 86 further extends toward pool of refrigerant
82 after covering tube bundle 78. In yet a further exemplary embodiment, hood 86 terminates
so that the hood does not totally cover the tube bundle, that is, substantially covers
the tube bundle.
[0023] As shown in FIGS. 6B and 6C, a pump 84 can be used to recirculate the pool of liquid
refrigerant 82 from the lower portion of the shell 76 via line 114 to distributor
80. As further shown in FIG. 6B, line 114 can include a regulating device 112 that
can be in fluid communication with a condenser (not shown). In another exemplary embodiment,
an ejector (not shown) can be employed to draw liquid refrigerant 82 from the lower
portion of shell 76 using the pressurized refrigerant from condenser 34, which operates
by virtue of the Bernoulli effect. The ejector combines the functions of a regulating
device 112 and a pump 84.
[0024] In an exemplary embodiment, one arrangement of tubes or tube bundles may be defined
by a plurality of uniformly spaced tubes that are aligned vertically and horizontally,
forming an outline that can be substantially rectangular. However, a stacking arrangement
of tube bundles can be used where the tubes are neither vertically or horizontally
aligned, as well as arrangements that are not uniformly spaced.
[0025] In another exemplary embodiment, different tube bundle constructions are contemplated.
For example, finned tubes (not shown) can be used in a tube bundle, such as along
the uppermost horizontal row or uppermost portion of the tube bundle. Besides the
possibility of using finned tubes, tubes developed for more efficient operation for
pool boiling applications, such as in "flooded" evaporators, may also be employed.
Additionally, or in combination with the finned tubes, porous coatings can also be
applied to the outer surface of the tubes of the tube bundles.
[0026] In a further exemplary embodiment, the cross-sectional profile of the evaporator
shell may be non-circular.
[0027] In an exemplary embodiment, a portion of the hood may partially extend into the shell
outlet.
[0028] In addition, it is possible to incorporate the expansion functionality of the expansion
devices of system 14 into distributor 80. In one exemplary embodiment, two expansion
devices may be employed. One expansion device is exhibited in the spraying nozzles
of distributor 80. The other expansion device, for example, expansion device 36, can
provide a preliminary partial expansion of refrigerant, before that provided by the
spraying nozzles positioned inside the evaporator. In an exemplary embodiment, the
other expansion device, that is, the non-spraying nozzle expansion device, can be
controlled by the level of liquid refrigerant 82 in the evaporator to account for
variations in operating conditions, such as evaporating and condensing pressures,
as well as partial cooling loads. In an alternative exemplary embodiment, expansion
device can be controlled by the level of liquid refrigerant in the condenser, or in
a further exemplary embodiment, a "flash economizer" vessel. In one exemplary embodiment,
the majority of the expansion can occur in the nozzles, providing a greater pressure
difference, while simultaneously permitting the nozzles to be of reduced size, therefore
reducing the size and cost of the nozzles.
[0029] FIG. 7 shows an exemplary embodiment of a distributor 142 that is configured to apply
a fluid entering the distributor 142 onto a tube bundle in a similar manner as previously
shown, such as FIG. 6B. Distributor 142 includes an enclosure 144 having an end 148
positioned to face a tube bundle (e.g., FIG. 6B) and an opposed end 150 facing away
from the tube bundle. Distributor 142 also includes an inlet 156 formed in end 150
and extending between terminus 152 and opposed terminus 154. End 148 includes an end
feature 158 with which at least one distribution device 146 or a plurality of distribution
devices 146 is operatively associated. In one embodiment, distribution device 146
includes an opening 160 (FIG. 9) formed in end feature 158 of end 148. As a result
of this arrangement, fluid 206 entering inlet 156 of enclosure 144, which may include
a two-phase mixture of vapor and liquid, is distributed along the length of enclosure
144 and exits enclosure 144 via distribution device(s) 146 as distributed fluid 208.
Due to the novel construction of enclosure 144, flow of distributed fluid 208 along
the length of enclosure 144 is improved, i.e., directed to flow more uniformly along
the length of the enclosure.
[0030] It is to be understood that one, two or more distributors 142 can be used with a
single tube bundle. In one embodiment, two or more distributors can have an overlapping
spray angle 166 of distributed fluid 208 (FIG. 11). In one embodiment, a tube bundle
can be divided into regions, such as vertically separated regions, with independent
distributors. For example, for a large tube bundle divided into vertically separated
regions, one or more distributors can be arranged between each region to provide improved,
multi-level wetting of the tubes of the tube bundle.
[0031] While shown in FIGS. 7-10 as being assembled from multiple pieces, such as by welding,
enclosure 144 can be extruded having a unitary or one-piece construction.
[0032] FIG. 10 shows a cross section taken along line 10-10 of FIG. 9 that extends through
an opening 160 formed in end feature 158 of end 148. End 148 extends to opposed enclosure
portions 168, 170. As shown in FIG. 10, enclosure portions 168, 170 are parallel to
each other and have a plane of symmetry 180 relative to each other. As further shown
in FIG. 10, the enclosure has a height 176 and a width 178. The term aspect ratio
of the enclosure refers to the height 176 divided by its width 178. The aspect ratio
of the enclosure can range between about 2:1 and about 6:1. As a result of a properly
sized aspect ratio, in combination with the size and spacing of openings 160, fluid
flow through the openings 160 of enclosure can be optimized, i.e., made more uniform
over the length of the enclosure over substantially an entire range of fluid pressures
associated with operation of associated with operation of the distributor of the present
disclosure.
[0033] For example, as shown collectively in FIGS. 8-10, inlet 156 has a length 194 between
about one sixth and one third of length 200. Inlet 156 is generally centered between
opposed end portions 196, 198. In one embodiment, adjacent openings 160 formed in
end feature 158 of end 148 have a substantially equal spacing 164 from each other
along length 200. In another embodiment, spacing 164 between at least a portion of
adjacent openings 160 associated with inlet 156 can be larger than spacing 202 between
at least a portion of adjacent openings 160 associated with end portion 196 and/or
can be larger than spacing 204 between at least a portion of adjacent openings 160
associated with the end portion 198, for promoting more uniform fluid flow through
the collective openings 160 along length 200 of enclosure 144. In one embodiment,
spacing 202 between at least a portion of adjacent openings 160 associated with end
portion 196 can be substantially evenly spaced relative to spacing 204 between at
least a portion of adjacent openings 160 associated with end portion 198. In one embodiment,
openings 160 include a substantially uniform width 162. In one embodiment, the end
of the kerf of openings 160 can be "squared off' or substantially rectangular, although
in another embodiment the end of the kerf can be curved or a combination of curved
and linear, in a similar manner as shown for end features 158, 258, 358, 458 in respective
FIGS. 11-14, as will be discussed in further detail below. In another embodiment,
openings 160 can have varying widths. Therefore, it is to be understood that the size
of the openings 160 corresponds to a combination of distance 186 from an end of the
kerf of opening 160 to a distal point of tangency 184 (FIG. 11) of the end feature
158 of the enclosure, also referred to as height, as well as width 162 (FIG. 10).
That is, if widths 162 of openings 160 are substantially equal to each other, the
size of openings 160 would be considered to be substantially equal if the height or
distance 186 of the openings were also substantially equal. In one embodiment, where
widths 162 of openings 160 are different from each other, then height or distance
186 of openings can be different from each other, but the size of the openings 160
can be substantially equal to each other, so long as the result is substantially uniform
fluid flow along the length 200 (FIG. 8) of the enclosure. In one embodiment, at least
two of openings 160 are substantially equal to each other or substantially evenly
sized.
[0034] Although enclosure portions 168, 170 are shown in FIG. 10 as generally parallel,
enclosure portion 168 can include an angular deviation 172, and/or enclosure portion
170 can include an angular deviation 174. As a result, enclosure portions 168, 170
can each deviate from between zero and about 45 degrees or any sub combination thereof
from parallel relative to each other, resembling a "V" shape. In one embodiment, angular
deviation 172 and/or angular deviation 174 can vary along the length of the enclosure,
if desired.
[0035] FIG. 11, which is an enlarged view of region 11 of FIG. 10, shows further details
of an exemplary end feature 158 of enclosure 144. As further shown in FIG. 11, feature
158 defines a curved or hemispherical profile having a radius or effective radius
or radial distance 189 and extending to opposed enclosure portions 168, 170. In one
embodiment, radius or effective radius or radial distance 189 can include one or more
curves having different radii of curvature. Effective radius or radius or radial distance
189 extends outwardly from a center point or point of coincidence 181 that is coincident
with a reference line 182 that is generally perpendicular to the opposed enclosure
portions 168, 170. As shown in FIG. 10, enclosure portions 168, 170 are parallel to
each other and have a plane of symmetry 180 relative to each other, and in one embodiment,
plane of symmetry 180 is coincident with reference line 182. In one embodiment, point
of coincidence 181 is not positioned in the center of enclosure 144. In one embodiment,
the enclosure does not have a plane of symmetry. Opening 160 includes edges 161, 163
that are associated with the ends of the kerf associated with opening 160, with edge
161 associated with and in close proximity to enclosure portion 168, and edge 163
associated with and in close proximity to enclosure portion 170. As further shown
in FIG. 11, a reference line 183 is generally perpendicular to opposed enclosure portions
168, 170 and extending through edges 161, 163. Reference line 182 is parallel to reference
line 183. A distal portion 187 of end feature 158 of end 148 relative to enclosure
portions 168, 170 includes a distal point of tangency 184 that is coincident with
a reference line 185 which is mutually parallel to reference lines 182, 183. The spacing
or effective spacing between edges 161, 163 of opening 160 and point of tangency 184
of distal portion 187 of end feature 158 as measured along reference line 185 yields
a distance 186. The spacing between reference line 182 that extends through point
of coincidence 181 and distal point of tangency 184, as measured along the reference
line 185, yields a distance 188. Distance 188 is greater than distance 186. That is,
the radius or effective radius or radial distance 189 associated with a distal tangential
portion, such as point of tangency 184 of end feature 158 (distance 188) is greater
than an effective spacing or spacing between edges 161, 163 associated with a distal
tangential portion, such as point of tangency 184 (distance 186). As a result, distributed
fluid flowing through openings 160 is constrained to a spray angle 166 of between
about 60 degrees and about 180 degrees, between about 90 degrees and about 180 degrees,
between about 120 degrees and about 180 degrees, between about 150 degrees and about
180 degrees, between about 160 degrees and about 180 degrees, between about 160 degrees
and about 170 degrees, between about 160 degrees and about 165 degrees, about 160
degrees, about 165 degrees, and about 170 degrees, which spray angle 166 remaining
relatively constant over substantially an entire range of fluid pressures associated
with operation of the distributor of a vapor compression system.
[0036] FIG. 12, which is an enlarged view of a region similar to region 11 of FIG. 10, shows
further details of an exemplary end feature 258 of enclosure 144. As further shown
in FIG. 12, feature 258 defines a squared off or rectangular profile comprised of
linear segments of the enclosure having an effective radius or effective radial distance
289 and extending to opposed enclosure portions 168, 170. Effective radius or effective
radial distance 289 extends outwardly from a center point or point of coincidence
281 that is coincident with a reference line 282 that is generally perpendicular to
the opposed enclosure portions 168, 170. In one embodiment, point of coincidence 281
is not positioned in the center of enclosure 144. In one embodiment, the enclosure
does not have a plane of symmetry. Opening 260 includes edges 261, 263 that are associated
with the ends of the kerf associated with opening 260, with edge 261 associated with
and in close proximity to enclosure portion 168, and edge 263 associated with and
in close proximity to enclosure portion 170. As further shown in FIG. 12, a reference
line 283 is generally perpendicular to opposed enclosure portions 168, 170 and extending
through edges 261, 263. Reference line 282 is parallel to reference line 283. A distal
portion 287 of end feature 258 of end 148 relative to enclosure portions 168, 170
includes a distal point of tangency 284 that is coincident with a reference line 285
which is mutually parallel to reference lines 282, 283. The spacing or effective spacing
between edges 261, 263 of opening 260 and point of tangency 284 of distal portion
287 of end feature 258 as measured along reference line 285 yields a distance 286.
The spacing between reference line 282 that extends through point of coincidence 281
and distal point of tangency 284, as measured along the reference line 285, yields
a distance 288. Distance 288 is greater than distance 286. That is, the effective
radius or effective radial distance 289 associated with a distal tangential portion,
such as point of tangency 284 of end feature 258 (distance 288) is greater than an
effective spacing or spacing between edges 161, 163 associated with distal tangential
portion, such as point of tangency 284 (distance 286). As a result, distributed fluid
flowing through openings 260 is constrained to a spray angle 166 (Fig 11) of between
about 60 degrees and about 180 degrees, between about 90 degrees and about 180 degrees,
between about 120 degrees and about 180 degrees, between about 150 degrees and about
180 degrees, between about 160 degrees and about 180 degrees, between about 160 degrees
and about 170 degrees, between about 160 degrees and about 165 degrees, about 160
degrees, about 165 degrees, and about 170 degrees, which spray angle 166 remaining
relatively constant over substantially an entire range of fluid pressures associated
with operation of the distributor of a vapor compression system.
[0037] FIG. 13, which is an enlarged view of a region similar to region 11 of FIG. 10, shows
further details of an exemplary end feature 358 of enclosure 144. As further shown
in FIG. 13, end feature 358 defines a "V" profile comprised of linear segments of
the enclosure having an effective radius or effective radial distance 389 and extending
to opposed enclosure portions 168, 170. Effective radius or effective radial distance
389 extends outwardly from a center point or point of coincidence 381 that is coincident
with a reference line 382 that is generally perpendicular to the opposed enclosure
portions 168, 170. In one embodiment, point of coincidence 381 is not positioned in
the center of enclosure 144. In one embodiment, the enclosure does not have a plane
of symmetry. Opening 360 includes edges 361, 363 that are associated with the ends
of the kerf associated with opening 360, with edge 361 associated with and in close
proximity to enclosure portion 168, and edge 363 associated with and in close proximity
to enclosure portion 170. As further shown in FIG. 13, a reference line 383 is generally
perpendicular to opposed enclosure portions 168, 170 and extending through edges 361,
363. Reference line 382 is parallel to reference line 383. A distal portion 387 of
end feature 358 of end 148 relative to enclosure portions 168, 170 includes a distal
point of tangency 384 that is coincident with a reference line 385 which is mutually
parallel to reference lines 382, 383. The spacing or effective spacing between edges
361, 363 of opening 360 and point of tangency 384 of distal portion 387 of end feature
358 as measured along reference line 385 yields a distance 386. The spacing between
reference line 382 that extends through point of coincidence 381 and distal point
of tangency 384, as measured along the reference line 385, yields a distance 388.
Distance 388 is greater than distance 386. That is, the effective radius or effective
radial distance 389 associated with a distal tangential portion, such as point of
tangency 384 of end feature 358 (distance 388) is greater than an effective spacing
or spacing between edges 361, 363 associated with distal tangential portion, such
as point of tangency 384 (distance 386). As a result, distributed fluid flowing through
openings 360 is constrained to a spray angle 166 (Fig 11) of between about 60 degrees
and about 180 degrees, between about 90 degrees and about 180 degrees, between about
120 degrees and about 180 degrees, between about 150 degrees and about 180 degrees,
between about 160 degrees and about 180 degrees, between about 160 degrees and about
170 degrees, between about 160 degrees and about 165 degrees, about 160 degrees, about
165 degrees, and about 170 degrees, which spray angle 166 remaining relatively constant
over substantially an entire range of fluid pressures associated with operation of
the distributor of a vapor compression system.
[0038] FIG. 14, which is an enlarged view of a region similar to region 11 of FIG. 10, shows
further details of an exemplary end feature 458 of enclosure 144. As further shown
in FIG. 14, feature 458 defines a lower portion of a "D" profile comprised of a combination
of linear and curved segments of the enclosure having an effective radius or effective
radial distance 489 and extending to opposed enclosure portions 168, 170. In one embodiment,
different arrangements or profiles of curved segments and linear segments can be used.
Effective radius or effective radial distance 489 extends outwardly from a center
point or point of coincidence 481 that is coincident with a reference line 482 that
is generally perpendicular to the opposed enclosure portions 168, 170. In one embodiment,
point of coincidence 481 is not positioned in the center of enclosure 144. In one
embodiment, the enclosure does not have a plane of symmetry. Opening 460 includes
edges 461, 463 that are associated with the ends of the kerf associated with opening
460, with edge 461 associated with and in close proximity to enclosure portion 168,
and edge 463 associated with and in close proximity to enclosure portion 170. As further
shown in FIG. 13, a reference line 483 is generally perpendicular to opposed enclosure
portions 168, 170 and extending through edges 461, 463. Reference line 482 is parallel
to reference line 483. A distal portion 487 of end feature 458 of end 148 relative
to enclosure portions 168, 170 includes a distal point of tangency 484 that is coincident
with a reference line 485 which is mutually parallel to reference lines 482, 483.
The spacing or effective spacing between edges 461, 463 of opening 460 and point of
tangency 484 of distal portion 487 of end feature 458 as measured along reference
line 485 yields a distance 486. The spacing between reference line 482 that extends
through point of coincidence 481 and distal point of tangency 484, as measured along
the reference line 485, yields a distance 488. Distance 488 is greater than distance
486. That is, the effective radius or effective radial distance 489 associated with
a distal tangential portion, such as point of tangency 484 of end feature 458 (distance
488) is greater than an effective spacing or spacing between edges 461, 463 associated
with a distal tangential portion, such as point of tangency 484 (distance 486). As
a result, distributed fluid flowing through openings 460 is constrained to a spray
angle 166 (Fig 11) of between about 60 degrees and about 180 degrees, between about
90 degrees and about 180 degrees, between about 120 degrees and about 180 degrees,
between about 150 degrees and about 180 degrees, between about 160 degrees and about
180 degrees, between about 160 degrees and about 170 degrees, between about 160 degrees
and about 165 degrees, about 160 degrees, about 165 degrees, and about 170 degrees,
which spray angle 166 remaining relatively constant over substantially an entire range
of fluid pressures associated with operation of the distributor of a vapor compression
system.
[0039] It is to be understood that lines 183, 283, 383, 483 associated with respective distances
186, 286, 386, 486 are not constrained to extend through each of respective edges
161 and 163, 261 and 263, 361 and 363, 461 and 463 of respective opening 160, 260,
360, 460. For example, in one embodiment, edges 161 and 163 of opening 160 can be
offset relative to line 183, such that line 183 represents an average distance 186
between corresponding edges 161, 163. However, lines 183, 283, 383, 483 and corresponding
respective distances 186, 286, 386, 486 to respective points of tangency 184, 284,
384, 484 are less than corresponding respective distances 188, 288, 388, 488 between
lines 182, 282, 382, 482 and corresponding respective distances 188, 288, 388, 488
to respective points of tangency 184, 284, 384, 484, in order to ensure a consistent,
controlled spray angle 166 (FIG. 11) of distributed fluid flow, for reasons previously
described above.
[0040] FIG. 15 shows an exemplary embodiment of distributor 142 having an axis 192 that
is curved, in contrast with a linear axis 190, which can provide improved fluid distribution
over some tube bundle arrangements as compared to a distributor having a straight
or linear axis, such as in combination with differently configured openings 160 (FIG.
8).
[0041] While only certain features and embodiments of the invention have been shown and
described, many modifications and changes may occur to those skilled in the art (e.g.,
variations in sizes, dimensions, structures, shapes and proportions of the various
elements, values of parameters (e.g., temperatures, pressures, etc.), mounting arrangements,
use of materials, colors, orientations, etc.) without materially departing from the
novel teachings and advantages of the subject matter recited in the claims. The order
or sequence of any process or method steps may be varied or re-sequenced according
to alternative embodiments. It is, therefore, to be understood that the appended claims
are intended to cover all such modifications and changes as fall within the invention.
Furthermore, in an effort to provide a concise description of the exemplary embodiments,
all features of an actual implementation may not have been described (i.e., those
unrelated to the presently contemplated best mode of carrying out the invention, or
those unrelated to enabling the claimed invention). It should be appreciated that
in the development of any such actual implementation, as in any engineering or design
project, numerous implementation-specific decisions may be made. Such a development
effort might be complex and time consuming, but would nevertheless be a routine undertaking
of design, fabrication, and manufacture for those of ordinary skill having the benefit
of this disclosure, without undue experimentation.
1. A distributor (80, 142) for use in a vapor compression system (14) comprising:
an enclosure (144) configured to be positioned in a heat exchanger (138) having a
tube bundle (78) comprising a plurality of tubes extending horizontally in the heat
exchanger (138); and
at least one distribution device (146) formed in an end (148) of the enclosure (144)
positioned to face the tube bundle (78), the at least one distribution device (146)
configured to apply a fluid (206) entering the distributor (80, 142) onto the tube
bundle (78), wherein the enclosure (144) has an aspect ratio between 2:1 and 6:1;
characterized in that
the end (148) of the enclosure (144) comprises an end feature (158) and the at least
one distribution device (146) comprises at least one opening (160) formed in the end
feature (158);
wherein the at least one opening (160) is configured and disposed to distribute fluid
at a spray angle (166) of between 60 degrees and 180 degrees over an entire range
of fluid pressures associated with operation of the distributor (80, 142) of the vapor
compression system (14); and
wherein the enclosure (144) further comprises a terminus (152) and an opposed terminus
(154) such that the fluid (206) is directed to flow more uniformly along a length
of the enclosure (144).
2. The distributor (80, 142) of claim 1, wherein the end feature (158) comprises at least
one of a curved profile, a linear profile, or a combination thereof
3. The distributor (80, 142) of claim 1, comprising parallel opposed portions (168, 170)
extending away from the end (148) of the enclosure (144).
4. The distributor (80, 142) of claim 3, wherein the opposed portions (168, 170) can
deviate from between zero degrees and 45 degrees from parallel to each other.
5. The distributor (80, 142) of claim 3, wherein a reference line (185) associated with
the end feature (158) and perpendicular to the opposed portions (168, 170) of the
end feature (158) is positioned a first distance (188) away from a distal tangential
portion (187) of the end feature (158), a second distance (186) is associated with
an effective spacing of the edges (163) formed in the at least one opening (160) and
a distal tangential portion (187) of the end feature (158), the first distance (188)
being greater than the second distance (186).
6. The distributor (80, 142) of claim 5, wherein a reference line (182) is coincident
with a center point (181) of an effective radius (189) of the end feature (158).
7. The distributor (80, 142) of claim 6, wherein a plane of symmetry (180) of the enclosure
(144) is coincident with the center point (181).
8. The distributor (80, 142) of claim 1, wherein the aspect ratio is between 2:1 and
4:1, and wherein the spray angle (166) is between 160 degrees and 170 degrees.
9. The distributor (80, 142) of claim 2, wherein the spray angle is 165 degrees.
10. The distributor (80, 142) of claim 2, wherein an inlet (156) is formed in an end (150)
of the enclosure (144) positioned to face away from the tube bundle (78), the inlet
(156) is configured to receive a fluid (206) into the enclosure (144), the inlet (156)
is centered relative to the length of the enclosure (144), and the inlet (156) is
between one sixth and one third of the length of the enclosure (144).
11. The distributor (80, 142) of claim 1, wherein the at least one distribution device
(146) comprises a plurality of openings (160) formed in the end feature (158) along
the length of the enclosure (144) and wherein the plurality of openings (160) formed
in the end feature (158) are evenly sized.
12. The distributor (80, 142) of claim 1, wherein:
- the plurality of openings (160) formed in the end feature (158) are evenly spaced
or
- the at least one distribution device (146) comprises a plurality of openings (160)
formed in the end feature (158), at least a portion of the plurality of openings (160)
having a first spacing (164) corresponding to a central segment of the length of the
enclosure (144) and at least a portion of the remaining openings (160) of the plurality
of openings (160) having a second spacing (202, 204) corresponding to at least one
end segment (196, 198) of the pair of end segments, the first spacing (164) is less
than the second spacing (202, 204).
13. A method of distributing fluid (206) in a vapor compression system (14), comprising:
providing an enclosure (144) configured to be positioned in a heat exchanger (138)
having a tube bundle (78) comprising a plurality of tubes extending horizontally in
the heat exchanger (138); and
forming at least one distribution device (146) in an end (148) of the enclosure (144)
positioned to face the tube bundle (78), the at least one distribution device (146)
configured to apply a fluid (206) entering the distributor (80, 142) onto the tube
bundle (78); and
operating the vapor compression system (14), wherein the enclosure (144) has an aspect
ratio between 2:1 and 6:1;
characterized in that
the end (148) of the enclosure (144) comprises an end feature (158) and the at least
one distribution device (146) comprises at least one opening (160) formed in the end
feature (158);
wherein the at least one opening (160) is configured and disposed to distribute fluid
at a spray angle (166) of between 60 degrees and 180 degrees over an entire range
of fluid pressures associated with operation of the distributor (80, 142) of the vapor
compression system (14); and
wherein the enclosure (144) further comprises a terminus (152) and an opposed terminus
(154) such that the fluid (206) is directed to flow more uniformly along a length
of the enclosure (144).
1. Verteiler (80, 142) zur Verwendung in einem Dampfkompressionssystem (14), Folgendes
umfassend:
eine Einfassung (144), die dafür gestaltet ist, in einem Wärmetauscher (138) positioniert
zu sein, der ein Rohrbündel (78) aufweist, das mehrere Rohre umfasst, die sich horizontal
in dem Wärmetauscher (138) erstrecken, und
mindestens eine Verteilungsvorrichtung (146), die in einem Ende (148) der Einfassung
(144) gebildet und zum Rohrbündel (78) weisend positioniert ist, wobei die mindestens
eine Verteilungsvorrichtung (146) dafür gestaltet ist, ein Fluid (206) zuzuführen,
das in den Verteiler (80, 142) auf dem Rohrbündel (78) eintritt, wobei die Einfassung
(144) ein Seitenverhältnis zwischen 2:1 und 6:1 aufweist,
dadurch gekennzeichnet, dass
das Ende (148) der Einfassung (144) ein Endmerkmal (158) umfasst und die mindestens
eine Verteilungsvorrichtung (146) mindestens eine Öffnung (160) umfasst, die in dem
Endmerkmal (158) gebildet ist,
wobei die mindestens eine Öffnung (160) dafür gestaltet und angeordnet ist, Fluid
in einem Sprühwinkel (166) zwischen 60 Grad und 180 Grad über einen gesamten Bereich
von Fluiddrücken zu verteilen, die mit dem Betrieb des Verteilers (80, 142) des Dampfkompressionssystems
(14) in Verbindung stehen, und
wobei die Einfassung (144) ferner einen Endpunkt (152) und einen gegenüberliegenden
Endpunkt (154) umfasst, so dass das Fluid (206) derart gerichtet ist, dass es gleichmäßiger
entlang einer Länge der Einfassung (144) strömt.
2. Verteiler (80, 142) nach Anspruch 1, wobei das Endmerkmal (158) mindestens eines von
einem gekrümmten Profil, einem linearen Profil oder einer Kombination daraus umfasst.
3. Verteiler (80, 142) nach Anspruch 1, parallele gegenüberliegende Abschnitte (168,
170) umfassend, die sich von dem Ende (148) der Einfassung (144) weg erstrecken.
4. Verteiler (80, 142) nach Anspruch 3, wobei die gegenüberliegenden Abschnitte (168,
170) zwischen null Grad und 45 Grad von ihrer Parallelität zueinander abweichen können.
5. Verteiler (80, 142) nach Anspruch 3, wobei eine Bezugslinie (185), die dem Endmerkmal
(158) zugeordnet ist und senkrecht zu den gegenüberliegenden Abschnitten (168, 170)
des Endmerkmals (158) liegt, in einer ersten Distanz (188) zu einem entfernten tangentialen
Abschnitt (187) des Endmerkmals (158), positioniert ist, wobei eine zweite Distanz
(186) einem effektiven Abstand zwischen den Rändern (163), die in der mindestens einen
Öffnung (160) gebildet sind, und einem entfernten tangentialen Abschnitt (187) des
Endmerkmals (158) zugeordnet ist, wobei die erste Distanz (188) größer als die zweite
Distanz (186) ist.
6. Verteiler (80, 142) nach Anspruch 5, wobei eine Bezugslinie (182) mit einem Mittelpunkt
(181) eines effektiven Radius (189) des Endmerkmals (158) zusammenfällt.
7. Verteiler (80, 142) nach Anspruch 6, wobei eine Symmetrieebene (180) der Einfassung
(144) mit dem Mittelpunkt (181) zusammenfällt.
8. Verteiler (80, 142) nach Anspruch 1, wobei das Seitenverhältnis zwischen 2:1 und 4:1
liegt und wobei der Sprühwinkel (166) zwischen 160 Grad und 170 Grad beträgt.
9. Verteiler (80, 142) nach Anspruch 2, wobei der Sprühwinkel 165 Grad beträgt.
10. Verteiler (80, 142) nach Anspruch 2, wobei in einem Ende (150) der Einfassung (144)
ein Einlass (156) gebildet ist, der positioniert ist, weg von dem Rohrbündel (78)
zu weisen, wobei der Einlass (156) dafür gestaltet ist, ein Fluid (206) zu empfangen,
das in die Einfassung (144) strömt, wobei der Einlass (156) im Verhältnis zur Länge
der Einfassung (144) mittig liegt und der Einlass (156) zwischen einem Sechstel und
einem Drittel der Länge der Einfassung (144) groß ist.
11. Verteiler (80, 142) nach Anspruch 1, wobei die mindestens eine Verteilungsvorrichtung
(146) mehrere Öffnungen (160) umfasst, die in dem Endmerkmal (158) entlang der Länge
der Einfassung (144) gebildet sind, und wobei die mehreren Öffnungen (160), die in
dem Endmerkmal (158) gebildet sind, von gleicher Größe sind.
12. Verteiler (80, 142) nach Anspruch 1, wobei:
- die mehreren Öffnungen (160), die in dem Endmerkmal (158) gebildet sind, gleichmäßig
beabstandet sind, oder
- die mindestens eine Verteilungsvorrichtung (146) mehrere Öffnungen (160) umfasst,
die in dem Endmerkmal (158) gebildet sind, wobei mindestens ein Teil der mehreren
Öffnungen (160) einen ersten Abstand (164) aufweisen, der einem mittigen Segment der
Länge der Einfassung (144) entspricht, und mindestens ein Teil der restlichen Öffnungen
(160) der mehreren Öffnungen (160) einen zweiten Abstand (202, 204) aufweisen, der
mindestens einem Endsegment (196, 198) des Paares von Endsegmenten entspricht, wobei
der erste Abstand (164) kleiner als der zweite Abstand (202, 204) ist.
13. Verfahren zum Verteilen von Fluid (206) in einem Dampfkompressionssystem (14), Folgendes
umfassend:
Bereitstellen einer Einfassung (144), die dafür gestaltet ist, in einem Wärmetauscher
(138) positioniert zu werden, der ein Rohrbündel (78) aufweist, das mehrere Rohre
umfasst, die sich horizontal in dem Wärmetauscher (138) erstrecken, und
Bilden mindestens einer Verteilungsvorrichtung (146) in einem Ende (148) der Einfassung
(144), positioniert, zum Rohrbündel (78) zu weisen, wobei die mindestens eine Verteilungsvorrichtung
(146) dafür gestaltet ist, ein Fluid (206) zuzuführen, das in den Verteiler (80, 142)
auf dem Rohrbündel (78) eintritt, und
Betreiben des Dampfkompressionssystems (14), wobei die Einfassung (144) ein Seitenverhältnis
zwischen 2:1 und 6:1 aufweist,
dadurch gekennzeichnet, dass
das Ende (148) der Einfassung (144) ein Endmerkmal (158) umfasst und die mindestens
eine Verteilungsvorrichtung (146) mindestens eine Öffnung (160) umfasst, die in dem
Endmerkmal (158) gebildet ist,
wobei die mindestens eine Öffnung (160) dafür gestaltet und angeordnet ist, Fluid
in einem Sprühwinkel (166) zwischen 60 Grad und 180 Grad über einen gesamten Bereich
von Fluiddrücken zu verteilen, die mit dem Betrieb des Verteilers (80, 142) des Dampfkompressionssystems
(14) in Verbindung stehen, und
wobei die Einfassung (144) ferner einen Endpunkt (152) und einen gegenüberliegenden
Endpunkt (154) umfasst, so dass das Fluid (206) derart gerichtet wird, dass es gleichmäßiger
entlang der Länge der Einfassung (144) strömt.
1. Distributeur (80, 142) destiné à être utilisé dans un système de compression de vapeur
(14), comprenant :
une enceinte (144) conçue pour être positionnée dans un échangeur de chaleur (138)
comportant un faisceau de tubes (78) comprenant une pluralité de tubes s'étendant
horizontalement dans l'échangeur de chaleur (138) ; et
au moins un dispositif de distribution (146) formé dans une extrémité (148) de l'enceinte
(144) qui est positionnée de manière à faire face au faisceau de tubes (78), l'au
moins un dispositif de distribution (146) étant conçu pour appliquer un fluide (206),
entrant dans le distributeur (80, 142), sur le faisceau de tubes (78), l'enceinte
(144) ayant un rapport de forme compris entre 2:1 et 6:1 ;
caractérisé en ce que
l'extrémité (148) de l'enceinte (144) comprend un élément caractéristique d'extrémité
(158) et l'au moins un dispositif de distribution (146) comprend au moins une ouverture
(160) ménagée dans l'élément caractéristique d'extrémité (158) ;
l'au moins une ouverture (160) étant conçue et disposée pour distribuer le fluide
à un angle de pulvérisation (166) compris entre 60 degrés et 180 degrés dans toute
une plage de pressions de fluide associées au fonctionnement du distributeur (80,
142) du système de compression de vapeur (14) ; et
l'enceinte (144) comprenant en outre une partie terminale (152) et une partie terminale
opposée (154) de sorte que le fluide (206) soit dirigé de manière à s'écouler plus
uniformément sur une longueur de l'enceinte (144).
2. Distributeur (80, 142) selon la revendication 1, l'élément caractéristique d'extrémité
(158) présentant au moins un profil parmi un profil incurvé, un profil linéaire et
une combinaison de ceux-ci.
3. Distributeur (80, 142) selon la revendication 1, comprenant des portions opposées
parallèles (168, 170) s'étendant depuis l'extrémité (148) de l'enceinte (144) .
4. Distributeur (80, 142) selon la revendication 3, les portions opposées (168, 170)
pouvant s'écarter l'une de l'autre entre zéro et 45 degrés par rapport à une parallèle.
5. Distributeur (80, 142) selon la revendication 3, une ligne de référence (185) associée
à l'élément caractéristique d'extrémité (158) et perpendiculaire aux portions opposées
(168, 170) de l'élément caractéristique d'extrémité (158) étant positionnée à une
première distance (188) d'une portion tangentielle distale (187) de l'élément caractéristique
d'extrémité (158), une deuxième distance (186) étant associée à un espacement effectif
des bords (163) bordés dans l'au moins une ouverture (160) et une portion tangentielle
distale (187) de l'élément caractéristique d'extrémité (158), la première distance
(188) étant supérieure à la deuxième distance (186).
6. Distributeur (80, 142) selon la revendication 5, une ligne de référence (182) coïncidant
avec un point central (181) d'un rayon effectif (189) de l'élément caractéristique
d'extrémité (158).
7. Distributeur (80, 142) selon la revendication 6, un plan de symétrie (180) de l'enceinte
(144) coïncidant avec le point central (181).
8. Distributeur (80, 142) selon la revendication 1, le rapport de forme étant compris
entre 2:1 et 4:1, et l'angle de pulvérisation (166) étant compris entre 160 degrés
et 170 degrés.
9. Distributeur (80, 142) selon la revendication 2, l'angle de pulvérisation étant de
165 degrés.
10. Distributeur (80, 142) selon la revendication 2, une entrée (156) étant formée dans
une extrémité (150) de l'enceinte (144) qui est positionnée à l'opposé du faisceau
de tubes (78), l'entrée (156) étant conçue pour recevoir un fluide (206) dans l'enceinte
(144), l'entrée (156) étant centrée par rapport à la longueur de l'enceinte (144),
et l'entrée (156) étant comprise entre un sixième et un tiers de la longueur de l'enceinte
(144).
11. Distributeur (80, 142) selon la revendication 1, l'au moins un dispositif de distribution
(146) comprenant une pluralité d'ouvertures (160) ménagées dans l'élément caractéristique
d'extrémité (158) sur la longueur de l'enceinte (144) et la pluralité d'ouvertures
(160) ménagées dans l'élément caractéristique d'extrémité (158) étant de taille uniforme.
12. Distributeur (80, 142) selon la revendication 1 :
- la pluralité d'ouvertures (160) ménagées dans l'élément caractéristique d'extrémité
(158) étant régulièrement espacées ou
- l'au moins un dispositif de distribution (146) comprenant une pluralité d'ouvertures
(160) ménagées dans l'élément caractéristique d'extrémité (158), au moins une portion
de la pluralité d'ouvertures (160) présentant un premier espacement (164) correspondant
à un segment central de la longueur de l'enceinte (144) et au moins une portion des
ouvertures restantes (160) de la pluralité d'ouvertures (160) présentant un deuxième
espacement (202, 204) correspondant à au moins un segment d'extrémité (196, 198) de
la paire de segments d'extrémité, le premier espacement (164) étant inférieur au deuxième
espacement (202, 204).
13. Procédé de distribution de fluide (206) dans un système de compression de vapeur (14),
comprenant les étapes suivantes :
fournir une enceinte (144) conçue pour être positionnée dans un échangeur de chaleur
(138) comportant un faisceau de tubes (78) comprenant une pluralité de tubes s'étendant
horizontalement dans l'échangeur de chaleur (138) ; et
former au moins un dispositif de distribution (146) dans une extrémité (148) de l'enceinte
(144) qui est positionnée pour faire face au faisceau de tubes (78), l'au moins un
dispositif de distribution (146) étant conçu pour appliquer un fluide (206), entrant
dans le distributeur (80, 142), sur le faisceau de tubes (78) ; et
faire fonctionner le système de compression de vapeur (14), l'enceinte (144) ayant
un rapport de forme compris entre 2:1 et 6:1 ;
caractérisé en ce que
l'extrémité (148) de l'enceinte (144) comprend un élément caractéristique d'extrémité
(158) et l'au moins un dispositif de distribution (146) comprend au moins une ouverture
(160) ménagée dans l'élément caractéristique d'extrémité (158) ;
l'au moins une ouverture (160) étant conçue et disposée pour distribuer le fluide
avec un angle de pulvérisation (166) compris entre 60 degrés et 180 degrés dans toute
une plage de pressions de fluide associées au fonctionnement du distributeur (80,
142) du système de compression de vapeur (14) ; et
l'enceinte (144) comprenant en outre une partie terminale (152) et une partie terminale
opposée (154) de sorte que le fluide (206) soit dirigé de manière à s'écouler plus
uniformément sur une longueur de l'enceinte (144).