U.S. patent number 3,866,439 [Application Number 05/384,879] was granted by the patent office on 1975-02-18 for evaporator with intertwined circuits.
This patent grant is currently assigned to Carrier Corporation. Invention is credited to William W. Bell, Jr., Rudy C. Bussjager.
United States Patent |
3,866,439 |
Bussjager , et al. |
February 18, 1975 |
EVAPORATOR WITH INTERTWINED CIRCUITS
Abstract
A refrigerant evaporator having a plurality of intertwined
refrigerant circuits which are connectable in alternative groups to
refrigerant distributors of a refrigeration system. Under low load
conditions, flow through one or more distributors is stopped to
remove from service the circuits connected to those distributors
and to present to the external heat exchange medium passing over
the evaporator refrigerant-carrying circuits selected according to
the nature of the circuit-distributor connections.
Inventors: |
Bussjager; Rudy C. (Minoa,
NY), Bell, Jr.; William W. (Marcellus, NY) |
Assignee: |
Carrier Corporation (Syracuse,
NY)
|
Family
ID: |
23519132 |
Appl.
No.: |
05/384,879 |
Filed: |
August 2, 1973 |
Current U.S.
Class: |
62/504;
62/524 |
Current CPC
Class: |
F25B
39/02 (20130101) |
Current International
Class: |
F25B
39/02 (20060101); F25b 039/02 () |
Field of
Search: |
;62/199,200,504,524,525,160,324 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Perlin; Meyer
Attorney, Agent or Firm: Curtin; J. Raymond
Claims
1. A compression refrigeration system including condenser means, a
plurality of parallel refrigerant lines for conveying condensed
refrigerant from said condenser means, refrigerant distribution
means in each of said parallel refrigerant lines, closing means for
selectively closing at least one of said parallel refrigerant lines
to refrigerant flow, and an evaporator including a plurality of
parallel heat exchange fins and a plurality of intertwined
refrigerant circuits running through the evaporator generally
transverse to said heat exchange fins, groups of said circuits
covering contiguous areas of said evaporator transverse to the
direction of flow of external heat exchange medium moving over said
evaporator, and said groups of circuits being connected to
different ones of said refrigerant distribution means, the group of
circuits connected to the distribution means in the refrigerant
line including said closing means being removable from service in
response to the closing of said closing means to substantially
reduce heat exchange between the external heat exchange medium
passing through the area covered by said latter group
2. A compression refrigeration system including condenser means, a
plurality of parallel refrigerant lines for conveying condensed
refrigerant from said condenser means, refrigerant distribution
means in each of said parallel refrigerant lines, closing means for
selectively closing at least one of said parallel refrigerant lines
to refrigerant flow, and an evaporator including a plurality of
parallel heat exchange fins and a plurality of refrigerant circuits
extending through the depth of the evaporator and including
connected parallel tubes running generally transverse to said heat
exchange fins, groups of said circuits covering in overlapping
fashion the area of said evaporator transverse to the flow of
external heat exchange medium moving over said evaporator, and
being connected to different ones of said distribution means, the
group connected to the distribution means in the refrigerant line
including said closing means being removable from service in
response to the closing of said closing means to substantially
reduce heat exchange between the
3. A compression refrigeration system according to claim 2 wherein
a
4. A compression refrigeration system according to claim 3 wherein
the external heat exchange medium enters said evaporator at a
particular side thereof, and said refrigerant circuits are arranged
to discharge
5. A compression refrigeration system according to claim 2 wherein
said closing means comprises valve means for selectively closing
said one refrigerant line to refrigerant flow.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates to refrigeration systems generally,
and in particular to evaporators used in such systems. More
specifically, the present invention relates to variable capacity,
multi-circuit refrigerant evaporators adapted for use in
refrigeration systems having a plurality of distributors for
distributing refrigerant to the various circuits.
2. Description of the Prior Art
Compression refrigeration systems generally comprise a compressor,
a condenser, an expansion device and an evaporator connected by
appropriate refrigerant lines to form a refrigeration circuit.
Refrigerant vapor is compressed by the compressor and fed to the
condenser where it releases heat, condenses, and flows through a
liquid line to an expansion device. The pressure of the refrigerant
is reduced as it passes through the expansion device, and it enters
the evaporator. The refrigerant in the evaporator absorbs ambient
heat and vaporizes, and is discharged into the suction line leading
to the compressor.
In order to improve the flow characteristics of refrigerant passing
through the evaporator, and in order to make fuller use of the heat
exchange surfaces (such as parallel, planar heat exchange fins) of
the evaporator, it is a common expedient to direct refrigerant
through the evaporator via a plurality of refrigerant circuits or
coils. Each circuit generally comprises a plurality of refrigerant
tubes which run transverse to the fin structure of the heat
exchanger, with the ends of appropriate tubes in each circuit being
connected by curved tubes or return bends. Refrigerant flowing
through a circuit makes several passes through the evaporator,
enabling it to absorb a significant amount of heat.
Refrigeration evaporators are frequently used to cool an ambient
heat exchange medium such as air, and it is common to force the air
or other heat exchange medium across the evaporator coils to
enhance the heat transfer at the heat exchange surfaces. It is
conventional to run each circuit across the full dimensions of the
evaporator transverse to the direction of flow of the external heat
exchange medium to increase the effect of the medium. In order to
equalize the air flow, and hence the air load, on each of the
circuits, it has been found advantageous to intertwine such
circuits in the evaporator. By this expedient, corresponding
portions of each circuit are exposed to the flow of the external
heat exchange medium at points of common temperature. The foregoing
is taught in U.S. Pat. Nos. 2,806,674 and 3,142,970.
Refrigerant evaporators of the foregoing types are frequently used
in situations where the loads upon the system may vary, such as in
air conditioning systems for commercial and industrial building
space. It is common to design the compressors and evaporators used
in these air conditioning systems according to the maximum load to
which they may be subjected, and it is known in the art to reduce
compressor capacity under low load conditions and to make a
corresponding reduction in the evaporator surface in service. The
effects of reducing the evaporator surface under the latter
conditions are to reduce the evaporator temperature to a useful
level for air conditioning and to maintain a sufficient rate of
refrigerant flow for proper oil return to the compressor. By
reducing the evaporator surface under low load conditions, the
compressor output can be reduced accordingly to prevent excessive
pressure in the evaporator. In U.S. Pat. No. 2,332,981, there is
disclosed an evaporator having ten rows of finned tubes. Five of
the rows are connected to a first distributor and a second group of
five rows are connected to a second distributor. Three tubes from
each of the two groups of five rows are additionally connected to
third and fourth distributors respectively. Valves in the liquid
refrigerant lines leading to each of the distributors can
selectively be closed to remove portions of the evaporator tube
surfaces from service during low load conditions.
One type of air conditioning system used in certain commercial
applications comprises a compression refrigeration system having a
large capacity commensurate with the space being conditioned, and
includes as one component a fan-coil unit. The fan-coil unit
includes an evaporator which absorbs heat from air passing
therethrough, and a fan moving the air through the evaporator. The
fan-coil unit is frequently used in systems having variable
capacities as described above, and the evaporator of these units is
sometimes provided with a plurality of refrigerant circuits, groups
of which are supplied with refrigerant from distributors connected
in turn to expansion devices. The refrigerant lines leading to the
distributors include valves which can be adjusted to close groups
of circuits passing through the unit to thereby reduce the capacity
of the evaporator. (Alternatively, each line can be supplied with
refrigerant by a separate compressor, in which case selected
circuits can be closed by shutting down the compressors supplying
those circuits.) There are two commonly known types of evaporators
adapted to have designated refrigerant circuits removed from
service under reduced load conditions. They are known in the art as
"face split evaporators," and as "row split evaporators." The
structure of evaporators incorporating these two forms of
"splitting" are different, so that it is necessary to design and
manufacture different evaporators for each type of split.
Evaporators designed to be face split include a plurality of
refrigerant circuits running back and forth across the length of
the unit. Each circuit includes a set of parallel tubes which are
often disposed at different positions in the depth of the unit,
tubes at each end of the evaporator being connected by return bends
to form the circuit. The circuits are arranged one over the other
along the height of the unit. (For this discussion, evaporators are
considered as having a horizontal length, a height which is
perpendicular to the flow of air over the unit and to the length,
and a depth which is parallel to the direction of air flow. The
flow of the external heat exchange medium is transverse to the area
defined by the length and height. It is understood that other
shapes and configurations are within the scope of the discussion.)
Adjacent groups of the circuits are connected to each of the
distributors. Thus for example, the circuits in the upper half of
the evaporator can be connected to one distributor and the circuits
in the lower half of the evaporator can be connected to a second
distributor. Refrigerant from the condenser passes through parallel
refrigerant lines and through expansion devices in those lines, and
thereafter through the distributors and into the various circuits
in the evaporator. Under low load conditions, the compressor of the
system operates at partial capacity, and flow through the line to
one of the distributors is closed, so that only the upper or lower
half of the evaporator coil receives refrigerant. Thus, only about
half of the air or other heat exchange medium passing through the
evaporator is cooled thereby.
In an evaporator adapted to be row split, the circuits do not run
throughout the depth of the evaporator, but rather are confined to
forward or rearward portions of the evaporator (the external heat
exchange medium passing first through the forward portions and then
through the rearward portions of the evaporator). An evaporator of
this type could thus comprise a plurality of refrigerant circuits
arranged in vertically oriented groups in the forward and rearward
halves of the evaporator. Each circuit has an inlet for receiving
refrigerant from a distributor and an outlet for discharging
refrigerant to a refrigerant vapor header leading to the suction
line of the compressor of the system. Air or other external heat
exchange medium passes first through the circuits in the forward
half of the unit and then through the circuits in the rearward half
of the unit, whereby the greatest amount of heat exchange
frequently occurs as the medium passes through the first group of
circuits. Each group of circuits is supplied with refrigerant by a
distributor associated with that group, and means are provided for
preventing refrigerant flow to at least one of the distributors
under low load conditions, whereby the circuit supplied with
refrigerant by that distributor can selectively be put out of
service. Unlike a face split evaporator, active circuits are
presented to the flow of external heat exchange medium across the
full evaporator area transverse to the flow even when a distributor
or compressor is not in service. Although more effective heat
transfer is achieved at partial load conditions with a conventional
row split evaporator than with a comparable face split evaporator,
the face split evaporator is more effective under full load. It is
desirable to superheat all refrigerant leaving the evaporator to
prevent liquid from passing to the compressor, and this can
effectively be done by having the relatively hot external heat
exchange medium (e.g., air) pass first over the exit tubes of the
evaporator since the temperature differential between the medium
and the evaporator tubes decreases as the medium proceeds through
the evaporator. It is feasible with the face split evaporator to
place the refrigerant discharge tubes of the evaporator at the
air-entering side of the evaporator to achieve the desired
superheat. However, all of the refrigerant discharge tubes cannot
be so arranged with the row split evaporator so that the superheat
capability is severely hampered.
A serious drawback of multi-circuit evaporators currently used in
face split and row split applications is that different evaporators
must be provided for each arrangement. This involves different
designs, and different manufacturing processes.
SUMMARY OF THE INVENTION
An object of the present invention is to provide an improved
variable capacity evaporator.
Another object of the invention is to provide a variable capacity
refrigerant evaporator having a plurality of circuits which can be
connected to a plurality of refrigerant distribution means in
alternative ways without altering the structure of the various
circuits, to effect alternative refrigerant flow paths through the
evaporator when the evaporator is operating at partial
capacity.
Still another object of the invention is to provide a refrigerant
evaporator having a plurality of substantially balanced refrigerant
circuits which can be connected to a plurality of refrigerant
distributors and which are selectively removable from service under
low load conditions.
A further object of the invention is the provision of a variable
capacity evaporator wherein the refrigerant discharge tubes are all
disposed at the entering side of the external heat exchange
medium.
Still another object of the invention is the provision of a
refrigeration system incorporating an evaporator having the
foregoing features, and refrigerant flow control apparatus for
cooperation with such evaporator.
Other objects will be apparent from the description to follow and
from the appended claims.
The foregoing objects are achieved by the provision of a
refrigerant evaporator which comprises a plurality of intertwined
refrigerant circuits which are so arranged that the evaporator can
be incorporated in a refrigeration system having a plurality of
refrigerant distributors, the distributors being connectable to the
circuits in alternative ways to effect alternative refrigerant flow
paths through the evaporator. Means are provided for withdrawing
selected circuits from service to reduce the capacity of the
evaporator under low heat load conditions. Depending on the nature
of the connection between the circuits and the distributors, and
between the circuits and refrigerant vapor headers, alternative
refrigerant-carrying circuits are presented to the external heat
exchange medium under low load
Each circuit includes a set of parallel refrigerant tubes running
transversely of the parallel planes of heat exchange fins included
in the evaporator. These fins advantageously comprise a plurality
of heat conductive metal sheets which substantially define the
length, height and depth of the evaporator. Curved connecting tubes
or return bends join the ends of the parallel tubes at the ends of
the evaporator to form the circuits. These circuits run across the
length of the evaporator and extend throughout the depth thereof.
Each circuit has an inlet which is connectable with a line leading
from a refrigerant distributor which receives refrigerant from an
expansion device. The inlets of groups of adjacent circuits can be
connected to a common distributor of a refrigeration system, there
being a distributor provided for supplying refrigerant to each
group of circuits. When a refrigerant flow leading to any of the
distributors is stopped, the group of circuits receiving
refrigerant from that distributor is removed from service.
Alternatively, the inlets of each of a group of circuits spaced
across the area of the evaporator normal to the flow of the
external heat exchange medium can be connected to a common
distributor. When the refrigerant flow to any of the distributors
is stopped, the capacity of the evaporator is reduced, but
refrigerant-carrying circuits remain across the full flow path of
the external heat exchange medium. The circuits are connected at
their outlet ends to refrigerant vapor headers which are in turn
connected to the compressor suction line, the nature of the latter
connection depending on the manner in which the distributors are
connected to the circuits.
BRIEF DESCRIPTION OF THE DRAWINGS
FIGS. 1 and 2 show in schematic form compression refrigeration
system employing an evaporator according to the present invention
which is connected to pairs of refrigerant distributors in the
systems in alternative manners.
DESCRIPTION OF THE PREFERRED EMBODIMENT
The description to follow relates to an evaporator having a
plurality of refrigerant circuits running therethrough and to a
refrigeration system incorporating such an evaporator. The
evaporator circuits are intertwined, and selected groups of the
circuits can be withdrawn from service depending on the manner in
which the circuits are connected to distributors supplying
refrigerant thereto. For the sake of this description, the
evaporator is presumed to have a conventional fin-tube construction
in that it comprises a large number of parallel, planar, heat
exchange fins through which tubes or other refrigerant conduits
extend transverse to the planes of the fins. In the drawings, end
views of an evaporator according to the invention are shown. Thus,
the portions of the tubes which are visible in the drawings are the
ends thereof and the curved connecting tubes or return bends which
connect the various parallel tubes together to form the refrigerant
circuits. The "depth" of the evaporator, as that term is used
herein, refers to the right to left dimension of the evaporator as
viewed in the drawings. The "height" of the evaporator is the top
to bottom dimension of the evaporator as viewed in the drawings.
Similarly, the "length" of the evaporator refers to that dimension
extending into the plane of the drawings.
Referring now to the drawings, there is shown in FIG. 1, a
compression refrigeration system including a compressor 1 from
which a refrigerant line leads to a condenser 3 having a liquid or
discharge line which terminates in parallel refrigerant lines 5 and
7. Refrigerant flow through line 5 can be controlled through a
valve 9 disposed in the line, and an expansion device 11 and a
conventional refrigerant distributor 13 are located in series in
line 5. A plurality of parallel refrigerant lines 15 lead from
distributor 13 to each of a group of refrigerant circuits running
through an evaporator 17. Similarly, an expansion device 19 and a
distributor 21 are disposed in series in refrigerant line 7, and a
group of parallel refrigerant lines 23 lead from distributor 21 to
each of a second group of refrigerant circuits running through
evaporator 17. The various refrigerant circuits terminate in
refrigerant vapor headers 25 which are in turn connected to the
inlet or suction line of compressor 1. Except for the manner in
which the circuits of evaporator 17 in FIG. 2 are connected to the
associated refrigerant distributors and refrigerant vapor headers,
the refrigeration system of FIG. 2 is identical to that of FIG. 1,
and corresponding elements of the system are shown with like
numbers having a prime designation.
With the exception of evaporator 17, the elements of the two
systems can be of any known type and can function in a normally
expected manner. Accordingly, compressors 1 and 1' discharge hot
compressed refrigerant vapor to condensers 3 and 3'. The
refrigerant gives up heat to an external heat exchange medium such
as air passing over the condenser and condenses to its liquid
state. The liquid refrigerant proceeds to parallel lines 5 and 7,
and 5' and 7', and through expansion devices 11 and 19, and 11' and
19'. The expansion devices function to reduce the pressure of
refrigerant passing therethrough, and can be of any appropriate
type such as thermal expansion valves or capillary tubes. The
expanded refrigerant proceeds through distributors 13 and 21, and
13' and 21'. These distributors can be, for example, fabricated
from solid materials and have a plurality of refrigerant passages
defined therein for distributing the refrigerant to each of the
selected refrigerant circuits in evaporator 17. The passages in
each of the distributors are joined with appropriate refrigerant
lines leading to the selected refrigerant circuits. Refrigerant
passes through the circuits of evaporator 17, and heat is
transferred to the refrigerant from an external heat exchange
medium such as air whose direction of movement is parallel to the
planes of the fins as indicated by the arrows. The refrigerant
vaporizes by virtue of this absorption of heat and, depending on
conditions, may be superheated. It is significant that the external
heat exchange medium first crosses those evaporator tubes at the
discharge side of the evaporator in both arrangements, so that the
likelihood of superheating the discharging refrigerant is
maximized. The refrigerant vapor is discharged from the evaporator
into refrigerant vapor headers 25 and 25', and thence into the
suction line leading back to compressor 1.
Evaporator 17 includes a plurality of refrigerant circuits 27-30
running therethrough. Each circuit is made up of parallel tubes
extending transversely through fins 26 and running across the
length of evaporator 17. Accordingly, circuit 27 includes parallel
tubes 31-34, circuit 28 includes tubes 35-38, circuit 29 includes
tubes 39-42 and circuit 30 includes parallel tubes 43-46. The tubes
of each circuit are joined by curved tubular connecting members or
return bends to form the circuit. These return bends are broadly
designated by the numeral 47. Pairs of refrigerant circuits 27 and
28, and 29 and 30, are intertwined. It is important to note that
the circuits shown have been depicted in a very simplified form for
the sake of the clarity of this description. Evaporator 17 is shown
as having four rows of aligned tubes (tubes 36, 32, 44 and 40
constituting one such row, for example). In practice, it could be
expected that other row arrangements would be found to be more
practical. Furthermore, only one horizontal tube from each circuit
is shown in each row. In practice, one could expect to have a
plurality of horizontal tubes from each circuit in each row, and
the extent of intertwining could be much greater or less than is
depicted.
When evaporator 17 is incorporated in a refrigeration system as
shown in FIG. 1, the inlets to the circuits in each of the upper
and lower halves of the evaporator are connected to a common
distributor. Thus, circuits 27 and 28 are supplied by distributor
13, and circuits 29 and 30 are supplied by distributor 21. When the
conditions are such that reduced cooling is required, the capacity
of compressor 1 is reduced by appropriate means such as by
deactivating some of the pistons if the compressor is of the
reciprocating type. In coordination with the reduction in the
capacity of compressor 1, valve 9 is closed. This diverts all of
the refrigerant flow through line 7, expansion device 19,
distributor 21 and circuits 29 and 30. In other words, the upper
portion of the evaporator is shut down and the evaporator is "face
split."
When evaporator 17 is connected to distributor 13' and 21' as
illustrated in FIG. 2, each distributor supplies refrigerant to
circuits disposed across the full area of the evaporator transverse
the direction of the flow of the external heat exchange medium.
Thus, the inlets to circuits 27 and 29 are connected to distributor
13', and the inlets to circuits 28 and 30 are connected to
distributor 21'.
When the refrigeration system shown in FIG. 2 is operated under low
load conditions and the capacity of compressor 1' has been reduced,
valve 9' is closed to divert the entire refrigerant flow from
condenser 3' into line 7', through expansion device 19' and into
distributor 21'. The expanded refrigerant is directed by
distributor 21' into lines 23' which lead to the inlets of circuits
28 and 30. Since circuits 28 and 30 are spaced from each other,
more effective use is made of fins 26 as contrasted both with the
arrangement of FIG. 1 (and with conventional row split evaporators)
when the systems operate under low load conditions, since there is
more fin area associated with each active tube. Moreover,
refrigerant-carrying circuits are presented to the external heat
exchange medium across the full area of its flow. At full capacity,
the arrangement in FIG. 2 provides a greater degree of superheat to
refrigerant leaving the evaporator than would a conventional row
split evaporator, because the external heat exchange medium crosses
the tubes from which refrigerant is discharged from the evaporator
when the medium is at its maximum temperature.
Evaporators according to the invention thus enjoy the benefits of
intertwined refrigerant circuitry, in particular the equal
distribution of loads on each of the circuits. Furthermore,
variable capacity evaporators according to the present invention
can be connected to refrigerant distributors in a variety of ways,
and separate designs are not required for each type of connection.
When the evaporator is connected to enable refrigerant-carrying
circuits to be presented to the external heat exchange medium
across a broad portion of the evaporator, more effective and
efficient operation is obtainable than with present row splitting
arrangements. Each circuit in evaporators according to the
invention takes an equal proportion of the load, so that when some
of the circuits are removed from service, the cooling effect of
each of the remaining circuits is evenly distributed and is readily
predictable.
Although the systems described above provide a set of distributors
for supplying refrigerant to groups of evaporator circuits, it is
within the scope of the invention to provide separate compressors
for each group of circuits. In the latter case, the refrigerant
valves can be dispensed with, and selected compressors can be shut
down under low load conditions to reduce the evaporator
capacity.
Evaporators according to the present invention find numerous
applications in various refrigeration systems. They find particular
use in direct expansion applications, since there is frequent
resort to reducing the number of evaporator circuits in service
under low load conditions.
The invention has been described in detail with particular
reference to a preferred embodiment thereof, but it will be
understood that variations and modifications can be effected within
the spirit and scope of the invention.
* * * * *