U.S. patent number 3,919,858 [Application Number 05/467,318] was granted by the patent office on 1975-11-18 for direct liquid refrigerant supply and return system.
This patent grant is currently assigned to Frick Company. Invention is credited to Robert C. Fish, Milton W. Garland.
United States Patent |
3,919,858 |
Garland , et al. |
November 18, 1975 |
Direct liquid refrigerant supply and return system
Abstract
A refrigerant system in which liquid halocarbon compound
refrigerant is delivered at pressures in excess of evaporation
pressure through metering outlets in a supply header of an
evaporator in a manner to provide uniform cooling throughout the
evaporator and utilizing a return header and liquid-vapor lift
apparatus to return vaporized and unevaporated refrigerant to an
accumulator-separator of the refrigeration system.
Inventors: |
Garland; Milton W. (Waynesboro,
PA), Fish; Robert C. (St. Louis, MO) |
Assignee: |
Frick Company (Waynesboro,
PA)
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Family
ID: |
26997664 |
Appl.
No.: |
05/467,318 |
Filed: |
May 6, 1974 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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352814 |
Apr 19, 1973 |
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Current U.S.
Class: |
62/498; 62/221;
62/235; 62/527; 165/174; 165/175; 62/525 |
Current CPC
Class: |
F28F
9/0263 (20130101); F25B 41/30 (20210101); F25C
3/02 (20130101); F25B 1/00 (20130101) |
Current International
Class: |
F28F
27/00 (20060101); F28F 27/02 (20060101); F25C
3/02 (20060101); F25C 3/00 (20060101); F25B
41/06 (20060101); F25B 1/00 (20060101); F25B
001/00 () |
Field of
Search: |
;62/218-221,235,333,498,524-527 ;165/174,175 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: O'Dea; William F.
Assistant Examiner: Capossela; Ronald C.
Attorney, Agent or Firm: Dowell, Jr.; A. Yates
Parent Case Text
CROSS-REFERENCE TO RELATED APPLICATIONS
This application is a countinuation-in-part of applicants'
application Ser. No. 352,814 filed April 19, 1973 and now
abandoned.
Claims
We claim:
1. A direct liquid refrigerant supply and return apparatus
including an evaporator for use with a refrigeration system having
an accumulator-separator, said apparatus comprising a supply header
having an inlet at one end for receiving pressurized liquid
refrigerant from the accumulator-separator, a plurality of heat
exchange pipes located substantially parallel with each other and
generally perpendicular to the supply header, each of said heat
exchange pipes being connected at one end to said supply header, a
return header in spaced generally parallel relationship to said
supply header, the opposite end of each of said heat exchange pipes
communicating with said return header, said return header having
discharge means at one end for discharging vaporized and
unevaporated refrigerant therefrom, said discharge means being
diametrically opposite said inlet to said supply header so that the
refrigerant flow paths from the inlet of said supply header through
said heat exchange pipes and said return header are substantially
of equal resistance, a vapor-liquid lift apparatus including a
receptacle for receiving vaporized and unevaporated refrigerant
from the discharge means of said return header, at least one
discharge pipe having one end extending into said receptacle and
the other end communicating with the accumulator-separator, the
unevaporated refrigerant being entrained in the vaporized
refrigerant within said receptacle, and means for moving the
vaporized refrigerant and the unevaporated refrigerant entrained
therein to the accumulator-separator at a velocity to maintain the
entrainment of the unevaporated refrigerant.
2. The structure of claim 1 including a plurality of metering means
carried by said supply header, each of said metering means having a
body with a bore and a counterbore concentric with said bore, plug
means having a metering orifice removably mounted in said bore,
said body having inlet means providing communication between said
supply header and said orifice and oulet means providing
communication between said counterbore and said heat exchange
pipes, and closure means removably mounted in said counterbore,
whereby said plug means may be selectively removed from said body
when said closure means is removed from said counterbore.
3. The structure of claim 2 including an insert mounted in said
metering orifice and being freely movable therein to prevent
clogging of said orifice.
4. The structure of claim 1 wherein said return header includes a
plurality of sections of progressively increasing diameters
eccentrically connected together along a common substantially
horizontal upper grade line and a stepped lower grade line, said
discharge means being adjacent the larger end of said return
header.
5. The structure of claim 1 in which said receptacle includes a
vertically disposed generally cylindrical side wall having a top
wall and a bottom wall fixed thereto.
6. The structure of claim 1 including a plurality of discharge
pipes having ends terminating at different elevations within said
receptacle to provide for varying capacities of flow to the
accumulator-separator.
7. The structure of claim 6 in which said discharge pipes are of
different diameter.
8. The structure of claim 6 in which the pipe for minimum capacity
has the least extension into said receptacle and each additional
pipe for increased capacity extends further into said receptacle.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention.
This invention relates generally to direct liquid refrigerant
systems of various kinds which may be used as the cooling means for
ice rinks and the like and relates specifically to a direct
refrigerant supply and return system which provides a substantially
uniform refrigerant flow through an evaporator having multiple,
single pass, parallel heat exchange pipes and which includes a
vapor-liquid lift apparatus to enable unevaporated refrigerant to
be entrained in the vaporized refrigerant and returned to an
accumulator-separator of a refrigeration system.
2. Description of the Prior Art.
Heretofore many efforts have been directed to providing refrigerant
systems for use in heat exchange substructures for ice rinks. In
the past, secondary or indirect fluid systems were utilized in
which indirect cooling of a surface area was primarily accomplished
by using a brine based solution as the heat exchange media which
had previously been cooled by a separate refrigerant system. In
recent years, indirect fluid systems have become outmoded in favor
of direct liquid refrigerant systems due to the expense and
inefficiencies of the indirect systems.
Direct liquid refrigerant systems have presented problems due to
the difficulty of maintaining substantially constant flow at
predetermined pressures throughout the heat exchange area of the
system. An example of structures in the prior art is U.S. Pat. No.
3,466,892 to Holmsten which discloses a multiple parallel pipe heat
exchange system. This patent discloses a centrally fed supply
header which supplies refrigerant fluid to a series of parallel
pipes that are connected at one end to the supply header and
connected at the opposite end to a return header having a central
discharge pipe. This structure at ordinary rates of flow does not
provide uniform refrigerant flow through the parallel pipes and
thus cooling effect fluctuates as the pressure variance causes a
change in the temperature gradient of the system. In order for such
a system to operate effectively, it is necessary to force the
refrigerant through the system at greater pressures and therefore
requires a greater refrigerant flow to obtain a more uniform
evaporation rate. Further, there has been no effort to insure a
steady and uniform return of the unevaporated liquid refrigerant
and vapors to the accumulator-separator in order to reduce or
prevent slugging of liquid being returned to the refrigeration
system. This slugging causes variations of pressure and liquid
levels in the system and subsequently these changes of the
operating conditions cause a change in the compression inlet
pressure and thereby place an irregular load on the compressor and
other components.
Other patents, such as U.S. Pat. No. 3,485,057 to Etter el al.
disclose systems for use with a multiple pass floor substructure
system using an ammonia refrigerant. This type of system is
satisfactory for use with inorganic compounds such as ammonia
(Refrigerant 717), where the individual pipes are grouped into feed
circuits of two or more pipes by means of return bends.
SUMMARY OF THE INVENTION
The present invention includes a supply and return system for use
with a halocarbon compound or other refrigerant to provide a direct
heat exchange structure for an ice rink or the like. The system has
a supply header which is flooded throughout its length and which
supplies liquid refrigerant to multiple, parallel, single pass heat
exchange pipes through self-cleaning metering valves. The supply
header feeds the heat exchange pipes in a diametric relationship to
the order in which the heat exchange pipe delivers vapor and
unevaporated liquid refrigerant to a return header, thereby
providing uniform cooling through the heat exchange area. The
system includes a stepped variable capacity return header which
maintains substantially constant pressure within the heat exchange
pipes and cooperates with a liquid-vapor lift apparatus in such a
manner as to allow unevaporated refrigerant to be entrained in the
vaporized refrigerant stream and thus return the unevaporated
refrigerant to an accumulator-separator of a refrigeration system
in an uninterrupted flow with the vaporized refrigerant.
It is an object of the invention to provide a direct, single pass,
multiple parallel pipe refrigerant supply and return system of a
type which is appropriate for use as the heat exchange substructure
in ice rinks.
Another object of the invention is to provide a system which
maintains an even distribution of refrigerant at nearly uniform
pressures throughout the multiple pipes of the evaporator.
It is a further object of this system to provide metering valves
which are self-cleaning and readily replaceable to insure a
constant and uniform delivery of refrigerant to the evaporator from
the supply header.
It is a further object of this invention to provide a system having
a liquid-vapor lift apparatus which allows unevaporated liquid
refrigerant to be raised a substantial height as an entrainment in
the vapor stream and discharged into the accumulator-separator of a
refrigerating system while the liquid flow rate to the supply
header remains relatively constant during compressor operation but
regardless of changing compressor capacity in response to changing
load.
BRIEF DESCRIPTION OF THE DRAWING
FIG. 1 is a top plan view of the direct liquid supply and return
system and schematically illustrating its relationship to an
accumulator-separator of a refrigeration system.
FIG. 2 is an enlarged side elevation of the return header of the
system.
FIG. 3 is an enlarged end view thereof.
FIG. 4 is an enlarged fragmentary section taken along the line 4--4
of FIG. 1.
FIG. 5 is an enlarged vertical section of the vaporliquid lift
assembly.
DESCRIPTION OF THE PREFERRED EMBODIMENT
With continued reference to the drawing, a refrigerant supply and
return system 10 is provided having an evaporator E for use with a
conventional refrigeration system 11 of an ice rink or the like 12.
As illustrated in FIG. 1, the conventional refrigeration system 11
includes a separating and delivery apparatus or
accumulator-separator 13 having a liquid control L and in which
vaporized refrigerant is separated from unevaporated liquid
refrigerant returning from the supply and return system 10. The
separated refrigerant vapor in the accumulator-separator 13 is
discharged through a suction line 14 to one or more compressors 15
which compress the vapor and discharge the same through lines 16,
oil separator 17, and line 18 to a condenser 19.
If desired, the compressors 15 could be provided with speed change
controls; however, two compressors normally are provided with each
compressor having a 50% capacity reduction. Thus, a system such as
that illustrated in FIG. 1, usually operates at 25%, 50%, 75% or
100% of its capacity depending upon operating conditions. From the
condenser the liquid refrigerant is discharged to a receiver 20 and
through a line 21 having an expansion control valve 22 to the
accumulator-separator 13. The liquid level control L regulates the
amount of liquid refrigerant which is discharged from the receiver
20 into the accumulator-separator 13 so that a substantially
constant liquid level is maintained therein.
In the preferred embodiment, refrigerant 22 (Chlorodifluoromethane)
is used as the direct heat exchange media. In FIG. 1, liquid
refrigerant is delivered under pressure by a pump P from the
accumulator-separator 13 to a supply pipe 26 having check valve C.
The supply pipe 26 carries the liquid refrigerant to the receiving
end or inlet 27 of supply header 28. The refrigerant feed to the
supply header is substantially constant and at a rate equal to at
least full capacity of the evaporator and usually at a greater
capacity.
With reference to FIG. 4, the supply header 28 is provided with a
plurality of generally upright discharge pipes 29 within each of
which is mounted a metering valve 30. Each metering valve 30
includes a body 31 having a vertically disposed tapered bore 32 and
a concentric tapered counterbore 33. The tapered bore 32 is
threaded for at least a portion of its length and threadedly
receives a metering plug 34 having an axial orifice 35 extending
entirely therethrough providing communication between the discharge
pipe 29 and the counterbore 33. A closure plug 36 is threadedly
received within the counterbore 33 to prevent the passage of
refrigerant to the exterior of the body 31.
The orifice 35 is of a size to permit a predetermined quantity of
liquid refrigerant to pass therethrough at a desired pressure. In
order to make certain that the orifice 35 remains open and to make
certain that there is no buildup of material which would restrict
flow therethrough, a wire insert 37 having outwardly bent ends 38
is inserted within the orifice 35 with such wire insert being
slightly longer than the length of the metering plug 34. Liquid
refrigerant passing through the orifice causes the wire insert 37
to jiggle or move in a haphazard manner to keep the orifice clean
of all materials. The wire insert is of a specific diameter
relative to the diameter of the orifice to permit a predetermined
quantity of refrigerant to pass through the orifice. It is
contemplated that by changing the diameter of the wire within the
orifices, the flow of refrigerant can be either increased or
further restricted. It is apparent that the metering plug 34 can be
easily removed from the body 31 to repair or replace the wire
insert 37 or to replace the metering plug 34 with another plug
having a different size orifice or wire insert.
The body 31 is provided with an enlargement or boss 39 at one side
and such boss has a bore 40 providing communication between the
counterbore 33 and the exterior of the body. A heat exchange pipe
41 of the evaporator E is connected to each of the metering valves
30 in communication with the outlet bore 40 and such pipes are
situated in a generally parallel relationship and disposed
generally perpendicular to the supply header 28.
The heat exchange pipes 41 are equally spaced along the length of
the supply header at intervals determined by the effective heat
exchange areas required with a spacing of approximately four inches
having been found satisfactory for an ice rink. Vapor and
unevaporated refrigerant are discharged from the heat exchange
pipes into a return or discharge header 42 disposed generally
perpendicular to such pipes and generally parallel to the supply
header 28.
The return header is of stepped eccentric construction having
sections 43, 44 and 45 of progressively larger diameters
respectively. These sections are situated along a common upper
grade line 46 which runs across the top of each of the sections 43,
44 and 45 and therefore has a stepped increasing lower grade line
47 defined by the bottom of each pipe. This configuration allows
for the necessary increase in capacity without pressure increase as
the flow is increased as each successive heat exchange pipe
discharges into the return header. Also, the stepped lower grade
line 47 permits the refrigerant to flow by gravity from sections
43-45 while allowing the heat exchange pipes to enter the return
header 42 at a common elevation.
Although the return header is described here as having three
sections, any desired number could be used to achieve the same
effect. Also, the lower grade line 47 could have a constant slope
from end to end.
The evaporated and unevaporated refrigerant which is received by
the return header 42 is discharged through a line 48 into a
vapor-liquid lift assembly 49. The discharge line 48 is located
diametrically opposite the inlet end 27 of the supply header 28 so
that all of the refrigerant flow paths are substantially equal in
resistance and the pressures within the heat exchange pipes 41 are
substantially constant. The lift assembly 49, FIG. 5, includes a
vertically positioned elongated generally cylindrical side wall 50
with a bottom wall 51 at one end and a top wall 52 at the other end
forming a receptacle for vaporized and unevaporated refrigerant.
The return line 48 enters the side wall at a point below the top
wall 52. A pair of vertically disposed discharge pipes 53 and 54
extend through the top wall 52 and are welded or otherwise
connected thereto. The vertical discharge pipes 53 and 54 are
positioned so that their intakes 55 and 56 respectively are below
the discharge line 48. The intake 56 of the vertical discharge pipe
is positioned below the intake 55 of the discharge pipe 53 with the
spacing between such intakes depending upon the quantity of
evaporated and unevaporated refrigerant being introduced to the
lift assembly 49 from the return header 42.
The vertical discharge pipe 53 normally is smaller in diameter than
the pipe 54 and is of a diameter such that when the compressors are
operating at minimum capacity, the suction through line 53
withdraws a mixture of vapor having liquid entrained therein at a
velocity of not less than 1,000 feet per minute. Such velocity is
necessary to insure that the liquid remains entrained in the
evaporated refrigerant and does not collect along the inner wall of
the vertical discharge pipe and run back into the lift
assembly.
When the compressors 15 are operating at minimum capacity, the
liquid level in the lift assembly is relatively high and the flow
of the liquid-vapor mixture is entirely through the upper discharge
line 53 since the suction is not sufficient to withdraw liquid
through line 54. As the capacity of the compressor is increased to
meet the load demands which cause increased vaporization in the
heat exchange pipes, the volume of flow in lines 53 and 54
increases.
At a predetermined compressor capacity, flow through pipe 54 is
initiated and a momentary slug of liquid may be discharged
therethrough depending upon the relative elevated spacing between
inlets 55 and 56 of pipes 53 and 54, respectively. At maximum
compressor capacity, the liquid level in the vapor-liquid lift is
such that the flow of the liquid-vapor mixture passes through both
pipes 53 and 54. In some instances, it may be advantageous to use
three or more vertical discharge pipes situated at various levels
in the lift assembly.
The purpose of the lift assembly 49 is to raise excess liquid which
is not evaporated, with a minimum of pressure penalty, from the
rink floor level into the accumulator-separator which usually is
much higher because of the structure of the building. Therefore, it
is necessary to provide a velocity of flow in one or more of the
vertical pipes 53 and 54 under any of the several capacity steps of
the compressors such that the velocity in any vertical pipe is not
less than 1,000 feet per minute thus providing a vertical movement
of unevaporated liquid as an entrainment in the vapor stream. As an
example, if the volume of liquid refrigerant delivered to the
supply header is 1.5 times greater than evaporation, then at full
load, the weight of the unevaporated liquid is equal to
approximately 50% of the weight of the vapor, but the volume of the
liquid is very small when compared to the vapor volume. The
unevaporated liquid refrigerant returned to the
accumulator-separator is inversely proportional to the load on the
evaporator but is readily moved with the vapor, providing vapor
velocity is never less than 1,000 feet per minute.
In the operation of the device, liquid refrigerant is pumped at a
constant volume from the accumulator-separator to the supply header
28 under all load conditions. From the supply header the liquid
refrigerant is fed to the plurality of heat exchange pipes 41
through the metering valves 30. The orifice 35 of each metering
valve and the wire insert therethrough permit a specific quantity
of liquid to be fed to each heat exchange pipe at a desired
pressure. The wire insert 37, being free to move with the orifice,
also functions to prevent the buildup of any material which would
tend to restrict the flow through the valves.
Under normal operating conditions, a portion of the liquid
refrigerant undergoes a change of state in the heat exchange pipe
41 as heat energy is absorbed from the ice rink or the like 12.
Subsequently, both evaporated and unevaporated refrigerant are
discharged into the return header 42.
The progressively larger diameters of the stepped eccentric return
header allows for the necessary increase in capacity without
pressure increase as the flow increases due to the discharge from
successive heat exchange pipes.
The unevaporated and evaporated refigerant is discharged from the
return header into the vapor-liquid lift apparatus 49. The
discharge from the return header is located diametrically opposite
the inlet to the supply header so that refrigerant flow paths
through the headers and each heat exchange pipe are substantially
equal, thereby aiding in maintaining a more uniform heat exchange
rate in the evaporator.
The refrigerant discharged into the vapor-liquid lift apparatus is
returned through discharge lines 54 and/or 53, in which suction is
created by the compressors 15, to the accumulator-separator as a
mixture of unevaporated refrigerant entrained in evaportated
refrigerant.
Systems of the type described herein usually have two compressors
each of which will have 50% capacity reduction, thus a minimum
capacity is 1/4 of the total capacity and the system may be
operated at 1/4 , 1/2 , 3/4 and full capacity by controls
responsive to operating pressure. The pressure differential
necessary to generate a desired velocity in the vertical lift pipes
is directly proportional to compressor pumping capacity. Thus, at
minimum capacity, the liquid level in the lift assembly is
relatively high and the vapor with unevaporated liquid refrigerant
entrained therein is raised entirely through the upper suction or
vertical line 53 at a rate of at least 1,000 feet per minute. At
1/2 capacity, the velocity in the vertical line 53 is increased and
the liquid level is lowered, but not sufficient to uncover the
vertical line 54. At substantially 3/4 capacity, the vertical line
54 is uncovered and vapor and unevaporated refrigerant flows
vertically through both lines 53 and 54 but the sizes have been
proportioned so that the velocity in each line is not less than
1,000 feet per minute. At full capacity the liquid level is further
lowered because of the increased flow in both of the vertical
pipes.
* * * * *