U.S. patent application number 13/433942 was filed with the patent office on 2013-03-28 for refrigerant circuit with integrated multi-mode thermal energy storage.
This patent application is currently assigned to Ice Energy, Inc.. The applicant listed for this patent is Brian Parsonnet, Dean L. Wiersma, Robert R. Willis, JR.. Invention is credited to Brian Parsonnet, Dean L. Wiersma, Robert R. Willis, JR..
Application Number | 20130074531 13/433942 |
Document ID | / |
Family ID | 46931911 |
Filed Date | 2013-03-28 |
United States Patent
Application |
20130074531 |
Kind Code |
A1 |
Parsonnet; Brian ; et
al. |
March 28, 2013 |
REFRIGERANT CIRCUIT WITH INTEGRATED MULTI-MODE THERMAL ENERGY
STORAGE
Abstract
Disclosed is a method and device for a refrigerant-based thermal
energy storage and cooling system with integrated multi-mode
refrigerant loops. The disclosed embodiments provide a
refrigerant-based thermal storage system with increased
versatility, reliability, lower cost components, reduced power
consumption and ease of installation.
Inventors: |
Parsonnet; Brian; (Fort
Collins, CO) ; Willis, JR.; Robert R.; (Fort Collins,
CO) ; Wiersma; Dean L.; (Fort Collins, CO) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Parsonnet; Brian
Willis, JR.; Robert R.
Wiersma; Dean L. |
Fort Collins
Fort Collins
Fort Collins |
CO
CO
CO |
US
US
US |
|
|
Assignee: |
Ice Energy, Inc.
Windsor
CO
|
Family ID: |
46931911 |
Appl. No.: |
13/433942 |
Filed: |
March 29, 2012 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
61470841 |
Apr 1, 2011 |
|
|
|
Current U.S.
Class: |
62/117 ;
62/434 |
Current CPC
Class: |
F25B 1/00 20130101; F25B
40/00 20130101; F25D 16/00 20130101 |
Class at
Publication: |
62/117 ;
62/434 |
International
Class: |
F25D 16/00 20060101
F25D016/00; F25B 1/00 20060101 F25B001/00 |
Claims
1. An integrated refrigerant-based thermal energy storage and
cooling system comprising: a refrigerant loop containing a
refrigerant comprising: a condensing unit, said condensing unit
comprising a compressor and a condenser; a thermal energy storage
module containing a thermal storage media and a primary heat
exchanger that facilitates heat transfer from said refrigerant to
said thermal storage media in a charge mode, and said primary heat
exchanger that facilitates heat transfer from said thermal storage
media to cool said refrigerant in a discharge mode; a storage
expansion device connected downstream of said condensing unit and
upstream of said thermal energy storage module; an evaporator
expansion device connected downstream of said condensing unit and
said thermal energy storage module; an evaporator connected
downstream of said evaporator expansion device; and, a valve system
that facilitates flow of refrigerant to said storage module from
said compressor or said condenser or said storage expansion device
or said evaporator, said valve system that facilitates flow of
refrigerant from said storage module to said compressor or said
condenser or said evaporator expansion device.
2. The system of claim 1 further comprising: a refrigerant
management vessel in fluid communication with, and located
downstream of said condenser.
3. The system of claim 1 wherein said storage expansion device is
chosen from the group consisting of a thermal expansion valve, an
electronic expansion valve, a static orifice, a capillary tube, and
a mixed-phase regulator.
4. The system of claim 1 wherein said evaporator expansion device
is chosen from the group consisting of a thermal expansion valve,
an electronic expansion valve, a static orifice, a capillary tube,
and a mixed-phase regulator.
5. The system of claim 1 wherein at least a portion of said thermal
storage media changes phase in said charge mode and said discharge
mode.
6. The system of claim 1 wherein said thermal storage media is a
eutectic material.
7. The system of claim 1 wherein said fluid is water.
8. The system of claim 1 wherein said thermal storage media does
not store heat in the form of latent heat.
9. The system of claim 1 wherein said evaporator is at least one
mini-split evaporator.
10. The system of claim 1 wherein said charge mode is operated
concurrent with and said discharge mode.
11. The system of claim 1 wherein said heat transfer medium is a
coolant.
12. The system of claim 1 wherein said heat transfer medium is a
refrigerant.
13. A method of providing cooling with an integrated thermal energy
storage and cooling system comprising: charging a thermal energy
storage module of said thermal energy storage and cooling system
during a first time period by: compressing and condensing a
refrigerant with a compressor and a condenser to create a
high-pressure refrigerant; dividing said a high-pressure
refrigerant downstream of said condenser into a first high-pressure
refrigerant and a second high-pressure refrigerant; expanding said
first said high-pressure refrigerant to provide storage cooling
with a thermal energy storage media via a primary heat exchanger
thereby producing a first expanded refrigerant, said primary heat
exchanger that is constrained within a thermal energy storage
module and in thermal communication with said storage media; and,
returning said first expanded refrigerant to said compressor;
expanding said second high-pressure refrigerant to provide cooling
in said evaporator thereby producing a second expanded refrigerant;
and, returning said expanded refrigerant and said secondary
expanded refrigerant to said compressor.
14. The method of claim 13 further comprising the step: bypassing
said thermal energy storage module of said thermal energy storage
and cooling system during a second time period by: compressing and
condensing said refrigerant with said compressor and said condenser
to create said high-pressure refrigerant; expanding said
high-pressure refrigerant to provide cooling in said evaporator and
produce expanded refrigerant; and, returning said expanded
refrigerant to said compressor.
15. The method of claim 13 further comprising the step: expanding
at least a portion of said high-pressure refrigerant with an
expansion device chosen from the group consisting of a storage
expansion device, an evaporator and an evaporator downstream of an
evaporator expansion device.
16. A method of providing cooling with an integrated thermal energy
storage and cooling system comprising: charging a thermal energy
storage module of said thermal energy storage and cooling system
during a first time period by: compressing and condensing a
refrigerant with a compressor and a condenser to create a
high-pressure refrigerant; expanding at least a portion of said
high-pressure refrigerant to produce expanded refrigerant and
provide storage cooling with a thermal energy storage media via a
primary heat exchanger, said primary heat exchanger that is
constrained within a thermal energy storage module and in thermal
communication with said storage media; and, returning said expanded
refrigerant to said compressor; discharging said thermal energy
storage module of said thermal energy storage and cooling system
during a second time period by: cooling and condensing a first
portion of a hot, high-pressure gas refrigerant from said
compressor with said storage cooling to produce warm liquid
refrigerant; condensing a second portion of said high-pressure
refrigerant from said compressor with said condenser; mixing said
first portion and said second portion and expanding said mixture to
provide cooling in an evaporator to produce said expanded
refrigerant; and, returning said expanded refrigerant to said
compressor.
17. The method of claim 16 further comprising the step: discharging
said thermal energy storage module of said thermal energy storage
and cooling system during a third time period by: cooling and
condensing a hot, high-pressure gas refrigerant from said
compressor with said storage cooling to produce warm liquid
refrigerant; condensing said warm liquid refrigerant with said
condenser to create subcooled refrigerant; expanding said subcooled
refrigerant to provide cooling in an evaporator to produce said
expanded refrigerant; and, returning said expanded refrigerant to
said compressor.
18. The method of claim 16 further comprising the step: discharging
said thermal energy storage module of said thermal energy storage
and cooling system during a third time period by: subcooling said
high-pressure refrigerant with said storage cooling to produce said
subcooled liquid refrigerant; expanding said subcooled liquid
refrigerant to provide cooling in said evaporator to produce said
expanded refrigerant; and, returning said expanded refrigerant to
said compressor.
19. The method of claim 16 further comprising the step: discharging
said thermal energy storage module of said thermal energy storage
and cooling system during a third time period by: expanding said
high-pressure refrigerant exiting said condenser to provide cooling
in said evaporator and produce expanded refrigerant; desuperheating
said expanded refrigerant with said storage cooling to produce
desuperheated refrigerant; and, returning said desuperheated
refrigerant to said compressor.
20. The method of claim 16 further comprising the step: bypassing
said thermal energy storage module of said thermal energy storage
and cooling system during a third time period by: compressing and
condensing said refrigerant with said compressor and said condenser
to create said high-pressure refrigerant; expanding said
high-pressure refrigerant to provide cooling in said evaporator and
produce expanded refrigerant; and, returning said expanded
refrigerant to said compressor.
21. The method of claim 16 further comprising the step: expanding
at least a portion of said high-pressure refrigerant with an
expansion device chosen from the group consisting of a storage
expansion device, an evaporator and an evaporator downstream of an
evaporator expansion device.
22. A method of providing cooling with an integrated thermal energy
storage and cooling system comprising: charging a thermal energy
storage module of said thermal energy storage and cooling system
during a first time period by: compressing and condensing a
refrigerant with a compressor and a condenser to create a
high-pressure refrigerant; expanding at least a portion of said
high-pressure refrigerant to produce expanded refrigerant and
provide storage cooling with a thermal energy storage media via a
primary heat exchanger, said primary heat exchanger that is
constrained within a thermal energy storage module and in thermal
communication with said storage media; and, returning said expanded
refrigerant to said compressor; discharging said thermal energy
storage module of said thermal energy storage and cooling system
during a second time period by: cooling and condensing a hot,
high-pressure gas refrigerant from said compressor with said
storage cooling to produce warm liquid refrigerant; condensing said
warm liquid refrigerant with said condenser to create subcooled
refrigerant; expanding said subcooled refrigerant to provide
cooling in an evaporator to produce said expanded refrigerant; and,
returning said expanded refrigerant to said compressor.
23. The method of claim 22 further comprising the step: discharging
said thermal energy storage module of said thermal energy storage
and cooling system during a second time period by: cooling and
condensing a first portion of a hot, high-pressure gas refrigerant
from said compressor with said storage cooling to produce warm
liquid refrigerant; condensing a second portion of said
high-pressure refrigerant from said compressor with said condenser;
mixing said first portion and said second portion and expanding
said mixture to provide cooling in an evaporator to produce said
expanded refrigerant; and, returning said expanded refrigerant to
said compressor.
24. The method of claim 22 further comprising the step: discharging
said thermal energy storage module of said thermal energy storage
and cooling system during a third time period by: subcooling said
high-pressure refrigerant with said storage cooling to produce said
subcooled liquid refrigerant; expanding said subcooled liquid
refrigerant to provide cooling in said evaporator to produce said
expanded refrigerant; and, returning said expanded refrigerant to
said compressor.
25. The method of claim 22 further comprising the step: discharging
said thermal energy storage module of said thermal energy storage
and cooling system during a third time period by: expanding said
high-pressure refrigerant exiting said condenser to provide cooling
in said evaporator and produce expanded refrigerant; desuperheating
said expanded refrigerant with said storage cooling to produce
desuperheated refrigerant; and, returning said desuperheated
refrigerant to said compressor.
26. The method of claim 22 further comprising the step: bypassing
said thermal energy storage module of said thermal energy storage
and cooling system during a third time period by: compressing and
condensing said refrigerant with said compressor and said condenser
to create said high-pressure refrigerant; expanding said
high-pressure refrigerant to provide cooling in said evaporator and
produce expanded refrigerant; and, returning said expanded
refrigerant to said compressor.
27. The method of claim 22 further comprising the step: expanding
at least a portion of said high-pressure refrigerant with an
expansion device chosen from the group consisting of a storage
expansion device, an evaporator and an evaporator downstream of an
evaporator expansion device.
28. A method of providing cooling with an integrated thermal energy
storage and cooling system comprising: charging a thermal energy
storage module of said thermal energy storage and cooling system
during a first time period by: compressing and condensing a
refrigerant with a compressor and a condenser to create a
high-pressure refrigerant; expanding at least a portion of said
high-pressure refrigerant to produce expanded refrigerant and
provide storage cooling with a thermal energy storage media via a
primary heat exchanger, said primary heat exchanger that is
constrained within a thermal energy storage module and in thermal
communication with said storage media; and, returning said expanded
refrigerant to said compressor; discharging said thermal energy
storage module of said thermal energy storage and cooling system
during a second time period by: subcooling said high-pressure
refrigerant with said storage cooling to produce said subcooled
liquid refrigerant; expanding said subcooled liquid refrigerant to
provide cooling in said evaporator to produce said expanded
refrigerant; and, returning said expanded refrigerant to said
compressor.
29. The method of claim 28 further comprising the step: discharging
said thermal energy storage module of said thermal energy storage
and cooling system during a second time period by: cooling and
condensing a first portion of a hot, high-pressure gas refrigerant
from said compressor with said storage cooling to produce warm
liquid refrigerant; condensing a second portion of said
high-pressure refrigerant from said compressor with said condenser;
mixing said first portion and said second portion and expanding
said mixture to provide cooling in an evaporator to produce said
expanded refrigerant; and, returning said expanded refrigerant to
said compressor.
30. The method of claim 28 further comprising the step: discharging
said thermal energy storage module of said thermal energy storage
and cooling system during a third time period by: cooling and
condensing a hot, high-pressure gas refrigerant from said
compressor with said storage cooling to produce warm liquid
refrigerant; condensing said warm liquid refrigerant with said
condenser to create subcooled refrigerant; expanding said subcooled
refrigerant to provide cooling in an evaporator to produce said
expanded refrigerant; and, returning said expanded refrigerant to
said compressor.
31. The method of claim 28 further comprising the step: discharging
said thermal energy storage module of said thermal energy storage
and cooling system during a third time period by: expanding said
high-pressure refrigerant exiting said condenser to provide cooling
in said evaporator and produce expanded refrigerant; desuperheating
said expanded refrigerant with said storage cooling to produce
desuperheated refrigerant; and, returning said desuperheated
refrigerant to said compressor.
32. The method of claim 28 further comprising the step: bypassing
said thermal energy storage module of said thermal energy storage
and cooling system during a third time period by: compressing and
condensing said refrigerant with said compressor and said condenser
to create said high-pressure refrigerant; expanding said
high-pressure refrigerant to provide cooling in said evaporator and
produce expanded refrigerant; and, returning said expanded
refrigerant to said compressor.
33. The method of claim 28 further comprising the step: expanding
at least a portion of said high-pressure refrigerant with an
expansion device chosen from the group consisting of a storage
expansion device, an evaporator and an evaporator downstream of an
evaporator expansion device.
34. A method of providing cooling with an integrated thermal energy
storage and cooling system comprising: charging a thermal energy
storage module of said thermal energy storage and cooling system
during a first time period by: compressing and condensing a
refrigerant with a compressor and a condenser to create a
high-pressure refrigerant; expanding at least a portion of said
high-pressure refrigerant to produce expanded refrigerant and
provide storage cooling with a thermal energy storage media via a
primary heat exchanger, said primary heat exchanger that is
constrained within a thermal energy storage module and in thermal
communication with said storage media; and, returning said expanded
refrigerant to said compressor; discharging said thermal energy
storage module of said thermal energy storage and cooling system
during a second time period by: expanding said high-pressure
refrigerant exiting said condenser to provide cooling in said
evaporator and produce expanded refrigerant; desuperheating said
expanded refrigerant with said storage cooling to produce
desuperheated refrigerant; and, returning said desuperheated
refrigerant to said compressor.
35. The method of claim 34 further comprising the step: discharging
said thermal energy storage module of said thermal energy storage
and cooling system during a second time period by: cooling and
condensing a first portion of a hot, high-pressure gas refrigerant
from said compressor with said storage cooling to produce warm
liquid refrigerant; condensing a second portion of said
high-pressure refrigerant from said compressor with said condenser;
mixing said first portion and said second portion and expanding
said mixture to provide cooling in an evaporator to produce said
expanded refrigerant; and, returning said expanded refrigerant to
said compressor.
36. The method of claim 34 further comprising the step: discharging
said thermal energy storage module of said thermal energy storage
and cooling system during a third time period by: cooling and
condensing a hot, high-pressure gas refrigerant from said
compressor with said storage cooling to produce warm liquid
refrigerant; condensing said warm liquid refrigerant with said
condenser to create subcooled refrigerant; expanding said subcooled
refrigerant to provide cooling in an evaporator to produce said
expanded refrigerant; and, returning said expanded refrigerant to
said compressor.
37. The method of claim 34 further comprising the step: discharging
said thermal energy storage module of said thermal energy storage
and cooling system during a third time period by: subcooling said
high-pressure refrigerant with said storage cooling to produce said
subcooled liquid refrigerant; expanding said subcooled liquid
refrigerant to provide cooling in said evaporator to produce said
expanded refrigerant; and, returning said expanded refrigerant to
said compressor.
38. The method of claim 34 further comprising the step: bypassing
said thermal energy storage module of said thermal energy storage
and cooling system during a third time period by: compressing and
condensing said refrigerant with said compressor and said condenser
to create said high-pressure refrigerant; expanding said
high-pressure refrigerant to provide cooling in said evaporator and
produce expanded refrigerant; and, returning said expanded
refrigerant to said compressor.
39. The method of claim 34 further comprising the step: expanding
at least a portion of said high-pressure refrigerant with an
expansion device chosen from the group consisting of a storage
expansion device, an evaporator and an evaporator downstream of an
evaporator expansion device.
40. A method of providing cooling with a thermal energy storage and
cooling system comprising: during a first time period: compressing
and condensing a refrigerant with a compressor and a condenser to
create a high-pressure refrigerant; expanding said high-pressure
refrigerant to produce expanded refrigerant and provide storage
cooling with a thermal energy storage media via a primary heat
exchanger, said primary heat exchanger that is constrained within a
thermal energy storage module and in thermal communication with
said storage media; and, returning said expanded refrigerant to
said compressor; during a second time period: compressing and
condensing said refrigerant with said compressor and said condenser
to create said high-pressure refrigerant; expanding a first portion
of said high-pressure refrigerant produce said first expanded
refrigerant and to provide storage cooling with said thermal energy
storage media via said primary heat exchanger, said primary heat
exchanger that is constrained within said thermal energy storage
module and in thermal communication with said storage media;
expanding a second portion of said high-pressure refrigerant to
provide cooling to an evaporator to produce said second expanded
refrigerant; and, returning said first expanded refrigerant and
said second expanded refrigerant to said compressor; during a third
time period: compressing said refrigerant with said compressor to
create hot, high-pressure gas refrigerant; cooling and condensing a
first portion of said hot, high-pressure gas refrigerant with said
storage cooling to produce warm liquid refrigerant; condensing a
second portion of said high-pressure refrigerant with said
condenser; mixing said first portion and said second portion and
expanding said mixture to provide cooling in an evaporator to
produce said expanded refrigerant; and, returning said expanded
refrigerant to said compressor; during a fourth time period:
compressing said refrigerant with said compressor to create said
hot, high-pressure gas refrigerant; cooling and condensing said
hot, high-pressure gas refrigerant with said storage cooling to
produce said warm liquid refrigerant; condensing said warm liquid
refrigerant with said condenser to create subcooled refrigerant;
expanding said subcooled refrigerant to provide cooling in an
evaporator to produce said expanded refrigerant; and, returning
said expanded refrigerant to said compressor; during a fifth time
period: compressing and condensing said refrigerant with said
compressor and said condenser to create said high-pressure
refrigerant; subcooling said high-pressure refrigerant with said
storage cooling to produce said subcooled liquid refrigerant;
expanding said subcooled liquid refrigerant to provide cooling in
said evaporator to produce said expanded refrigerant; and,
returning said expanded refrigerant to said compressor; during a
sixth time period: compressing and condensing said refrigerant with
said compressor and said condenser to create said high-pressure
refrigerant; expanding said high-pressure refrigerant to provide
cooling in said evaporator and produce expanded refrigerant;
desuperheating said expanded refrigerant with said storage cooling
to produce desuperheated refrigerant; and, returning said
desuperheated refrigerant to said compressor; during a seventh time
period; compressing and condensing said refrigerant with said
compressor and said condenser to create said high-pressure
refrigerant; expanding said high-pressure refrigerant to provide
cooling in said evaporator and produce expanded refrigerant;
superheating said expanded refrigerant with said storage media to
produce superheated refrigerant; and, returning said superheated
refrigerant to said compressor; during an eighth time period;
compressing and condensing said refrigerant with said compressor
and said condenser to create said high-pressure refrigerant;
expanding said high-pressure refrigerant to provide cooling in said
evaporator and produce expanded refrigerant; and, returning said
expanded refrigerant to said compressor.
Description
CROSS REFERENCE TO RELATED APPLICATION
[0001] This application is based upon and claims the benefit of
U.S. provisional application No. 61/470,841, entitled "Refrigerant
Circuit with Integrated Multi-Mode Thermal Energy Storage," filed
Apr. 1, 2011 and the entire disclosures of which is hereby
specifically incorporated by reference for all that it discloses
and teaches.
BACKGROUND OF THE INVENTION
[0002] With the increasing demands on peak demand power
consumption, Thermal Energy Storage (TES) has been utilized to
shift air conditioning power loads to off-peak times and rates. A
need exists not only for load shifting from peak to off-peak
periods, but also for increases in air conditioning unit capacity
and efficiency. Current air conditioning units having energy
storage systems have had limited success due to several
deficiencies, including reliance on water chillers that are
practical only in large commercial buildings and have difficulty
achieving high-efficiency.
[0003] In order to commercialize advantages of thermal energy
storage in large and small commercial buildings, thermal energy
storage systems must have minimal manufacturing costs, maintain
maximum efficiency under varying operating conditions, have minimal
implementation and operation impact and be suitable for multiple
refrigeration or air conditioning applications.
[0004] Systems for providing stored thermal energy have been
previously contemplated in U.S. Pat. No. 4,735,064, U.S. Pat. No.
5,225,526, both issued to Harry Fischer, U.S. Pat. No. 5,647,225
issued to Fischer et al., U.S. Pat. No. 7,162,878 issued to
Narayanamurthy et al., U.S. Pat. No. 7,854,129 issued to
Narayanamurthy, U.S. Pat. No. 7,503,185 issued to Narayanamurthy et
al., U.S. Pat. No. 7,827,807 issued to Narayanamurthy et al., U.S.
Pat. No. 7,363,772 issued to Narayanamurthy, U.S. Pat. No.
7,793,515 issued to Narayanamurthy, U.S. patent application Ser.
No. 11/837,356 filed Aug. 10, 2007 by Narayanamurthy et al.,
application Ser. No. 12/324,369 filed Nov. 26, 2008 by
Narayanamurthy et al., U.S. patent application Ser. No. 12/371,229
filed Feb. 13, 2009 by Narayanamurthy et al., U.S. patent
application Ser. No. 12/473,499 filed May 28, 2009 by
Narayanamurthy et al., and U.S. patent application Ser. No.
12/335,871 filed Dec. 16, 2008 by Parsonnet et al. All of these
patents and applications utilize ice storage to shift air
conditioning loads from peak to off-peak electric rates to provide
economic justification and are hereby incorporated by reference
herein for all they teach and disclose.
SUMMARY OF THE INVENTION
[0005] An embodiment of the present invention may therefore
comprise: an integrated refrigerant-based thermal energy storage
and cooling system comprising: a refrigerant loop containing a
refrigerant comprising: a condensing unit, the condensing unit
comprising a compressor and a condenser; a thermal energy storage
module containing a thermal storage media and a primary heat
exchanger that facilitates heat transfer from the refrigerant to
the thermal storage media in a charge mode, and the primary heat
exchanger that facilitates heat transfer from the thermal storage
media to cool the refrigerant in a discharge mode; a storage
expansion device connected downstream of the condensing unit and
upstream of the thermal energy storage module; an evaporator
expansion device connected downstream of the condensing unit and
the thermal energy storage module; an evaporator connected
downstream of the evaporator expansion device; and, a valve system
that facilitates flow of refrigerant to the storage module from the
compressor or the condenser or the storage expansion device or the
evaporator, the valve system that facilitates flow of refrigerant
from the storage module to the compressor or the condenser or the
evaporator expansion device.
[0006] An embodiment of the present invention may also comprise: a
method of providing cooling with a thermal energy storage and
cooling system comprising: during a first time period: compressing
and condensing a refrigerant with a compressor and a condenser to
create a high-pressure refrigerant; expanding the high-pressure
refrigerant to produce expanded refrigerant and provide storage
cooling with a thermal energy storage media via a primary heat
exchanger, the primary heat exchanger that is constrained within a
thermal energy storage module and in thermal communication with the
storage media; and, returning the expanded refrigerant to the
compressor; during a second time period: compressing and condensing
the refrigerant with the compressor and the condenser to create the
high-pressure refrigerant; expanding a first portion of the
high-pressure refrigerant to produce the first expanded refrigerant
and to provide storage cooling with the thermal energy storage
media via the primary heat exchanger, the primary heat exchanger
that is constrained within the thermal energy storage module and in
thermal communication with the storage media; expanding a second
portion of the high-pressure refrigerant to provide cooling to an
evaporator to produce the second expanded refrigerant; and,
returning the first expanded refrigerant and the second expanded
refrigerant to the compressor; during a third time period:
compressing the refrigerant with the compressor to create hot,
high-pressure gas refrigerant; cooling and condensing a first
portion of the hot, high-pressure gas refrigerant with the storage
cooling to produce warm liquid refrigerant; condensing a second
portion of the high-pressure refrigerant with the condenser; mixing
the first portion and the second portion and expanding mixture to
provide cooling in an evaporator to produce the expanded
refrigerant; and, returning the expanded refrigerant to the
compressor; during a fourth time period: compressing the
refrigerant with the compressor to create the hot, high-pressure
gas refrigerant; cooling and condensing the hot, high-pressure gas
refrigerant with the storage cooling to produce the warm liquid
refrigerant; condensing the warm liquid refrigerant with the
condenser to create subcooled refrigerant; expanding the subcooled
refrigerant to provide cooling in an evaporator to produce the
expanded refrigerant; and, returning the expanded refrigerant to
the compressor; during a fifth time period: compressing and
condensing the refrigerant with the compressor and the condenser to
create the high-pressure refrigerant; subcooling the high-pressure
refrigerant with the storage cooling to produce subcooled liquid
refrigerant; expanding the subcooled liquid refrigerant to provide
cooling in the evaporator to produce the expanded refrigerant; and,
returning the expanded refrigerant to the compressor; during a
sixth time period: compressing and condensing the refrigerant with
the compressor and the condenser to create the high-pressure
refrigerant; expanding the high-pressure refrigerant to provide
cooling in the evaporator and produce expanded refrigerant;
desuperheating the expanded refrigerant with the storage cooling to
produce desuperheated refrigerant; and, returning the desuperheated
refrigerant to the compressor; compressing and condensing the
refrigerant with the compressor and the condenser to create the
high-pressure refrigerant; expanding the high-pressure refrigerant
to provide cooling in the evaporator and produce expanded
refrigerant; superheating the expanded refrigerant with the storage
media to produce the superheated refrigerant; and, returning
superheated refrigerant to the compressor; during an eighth time
period; compressing and condensing the refrigerant with the
compressor and the condenser to create the high-pressure
refrigerant; expanding the high-pressure refrigerant to provide
cooling in the evaporator and produce expanded refrigerant;
returning the expanded refrigerant to the compressor.
BRIEF DESCRIPTION OF THE DRAWINGS
[0007] In the drawings,
[0008] FIG. 1 schematically illustrates an embodiment of a
refrigerant circuit with integrated multi-mode thermal energy
storage.
[0009] FIG. 2 is a schematic illustration of the valve conditions
for the embodiment of a thermal energy storage refrigerant circuit
capable of multiple charging and discharging modes.
[0010] FIG. 3 schematically illustrates a configuration of an
embodiment of a thermal energy storage refrigerant circuit with
integrated trickle charge loop.
[0011] FIG. 4 schematically illustrates a configuration of an
embodiment of a thermal energy storage refrigerant circuit with
full capacity charge loop.
[0012] FIG. 5 schematically illustrates a configuration of an
embodiment of a thermal energy storage refrigerant circuit with
parallel condenser discharge loop.
[0013] FIG. 6 schematically illustrates a configuration of an
embodiment of a thermal energy storage refrigerant circuit with hot
vapor desuperheater discharge loop.
[0014] FIG. 7 schematically illustrates a configuration of an
embodiment of a thermal energy storage refrigerant circuit with
warm liquid subcooler discharge loop.
[0015] FIG. 8 schematically illustrates a configuration of an
embodiment of a thermal energy storage refrigerant circuit with
cold vapor desuperheater discharge loop.
[0016] FIG. 9 schematically illustrates a configuration of an
embodiment of a thermal energy storage refrigerant circuit with
suction line charge loop.
DETAILED DESCRIPTION OF THE INVENTION
[0017] While this invention is susceptible to embodiment in many
different forms, it is shown in the drawings, and will be described
herein in detail, specific embodiments thereof with the
understanding that the present disclosure is to be considered as an
exemplification of the principles of the invention and is not to be
limited to the specific embodiments described.
[0018] FIG. 1 illustrates an embodiment of a refrigerant circuit
with integrated multi-mode thermal energy storage. The embodiments
shown may function with or without an accumulator vessel (surge
vessel) or URMV 102 (universal refrigerant management vessel), and
is depicted in FIG. 1 with the vessel in place.
[0019] As illustrated in FIG. 1, a variety of modes may be utilized
in the system shown to provide cooling in various conventional or
non-conventional air conditioning/refrigerant applications and
utilized with an integrated condenser/compressor/evaporator (e.g.,
off-the-shelf unit or original equipment manufactured [OEM]) as
either a retrofit to an existing system or a completely integrated
new install. In this embodiment, three charge modes, four discharge
modes and one bypass mode are possible with the system as shown.
These modes of charging and discharging the storage module include
trickle charge, full-capacity charge, parallel condenser discharge,
hot vapor desuperheater discharge, warm liquid subcooler discharge,
cold vapor desuperheater discharge and suction line charges.
[0020] The charging modes utilize a compressor 110 to compress
cold, low pressure refrigerant gas to hot, high-pressure gas. This
refrigerant passes through valve V1 122 to a condenser 112 which
removes much of the heat in the gas and discharges the heat to the
atmosphere. The refrigerant leaves the condenser 112 as a warm,
high-pressure liquid refrigerant delivered through a high-pressure
liquid supply line where a portion of the warm liquid refrigerant
is diverted by valve V3 126 to valve V4 128, which directs the
diverted refrigerant through the storage expansion device 118. The
storage expansion device 118 reduces the pressure of the warm
liquid refrigerant to generate a cold mixed-phase refrigerant,
which is directed to the heat exchanger 170 within the storage
module 116.
[0021] This storage expansion device 118 may be a conventional or
non-conventional thermal expansion valve, a static orifice, a
capillary tube, a mixed-phase regulator and surge vessel
(reservoir), or the like. In this mode, the heat exchanger 170 in
the storage module 116 acts as an evaporator where the cold
mixed-phase refrigerant absorbs heat from the storage media 160
that surrounds the heat exchanger 170 and vaporizes. The liquid
refrigerant transfers cooling to thermal energy storage media 160
within the thermal energy storage module 116 (as shown, but not
limited by way of example via a primary heat exchanger 170 within
an insulated tank). Low-pressure vapor phase refrigerant is then
returned to the compressor 110 via valve V7 134 where it is mixed
with the portion of the cold vapor refrigerant returning to
compressor 110 via valve V6 132 from the evaporator 114 that was
split at valve V3 126 and passed through valve V5 130 and an
evaporator expansion device 120. As with the storage expansion
device 118, evaporator expansion device 120 may be a conventional
or non-conventional thermal expansion valve, a static orifice, a
capillary tube, a mixed-phase regulator and surge vessel
(reservoir), or the like.
[0022] In order to meter the amount of refrigerant that is split by
valve V3 126, a specialized valve and controller that modulates
based on downstream pressures, for example, may be used to split
the amount of refrigerant that is diverted to provide immediate
cooling through evaporator 114 and the amount diverted to TES for
providing cooling capacity, which may be utilized at a later time.
Alternatively, the storage media 160 used in the storage module 116
can be selected in order to match the refrigerant evaporating
temperature of the storage module 116 to that of the evaporator
114, effectively matching the pressure drop across the storage
expansion device 118 and evaporator expansion device 120 resulting
in a self-metering trickle charge configuration.
[0023] The thermal energy storage unit 116 shown in FIG. 1 may
typically comprise an insulated tank that houses the primary heat
exchanger 170 surrounded by a storage media 160 (e.g., solid,
liquid coolant, eutectic or liquid phase material and/or solid
phase material or the like [fluid/ice] depending on the current
system mode). The primary heat exchanger 170 may typically further
comprise a lower header assembly connected to an upper header
assembly with a series of freezing and discharge coils to make a
fluid/vapor loop within the insulated tank. Such systems are
disclosed in the patents and applications referred to above, which
are also incorporated by reference.
[0024] When operating in full-capacity charge mode, the compressor
110 is energized to compress cold, low pressure refrigerant gas to
hot, high-pressure gas. This refrigerant passes through valve V1
122 and to a condenser 112, which removes much of the heat in the
gas and discharges the heat to the atmosphere. The refrigerant
leaves the condenser 112 as a warm, high-pressure liquid
refrigerant delivered through a high-pressure liquid supply line
where the entirety of the warm liquid refrigerant is diverted by
valve V3 126 to valve V4 128, which directs the diverted
refrigerant through the storage expansion device 118. Here, as in
the previously described trickle charge mode, the storage expansion
device 118 reduces the pressure of the warm liquid refrigerant to
generate a cold mixed-phase refrigerant. In this mode, the heat
exchanger 170 within the storage module 116 also acts as an
evaporator where the cold mixed-phase refrigerant absorbs heat from
the storage media 160 and vaporizes and transfers cooling to
thermal energy storage media 160 within the thermal energy storage
module 116. Low-pressure vapor phase refrigerant is then returned
to the compressor 110 via valve V7 134. Thus, the entirety of the
cooling provided by the compressor 110 and condenser 112 (typical
conventional air conditioning or refrigeration unit) is
transmitted, in one contemplated embodiment, from the heat
exchanger 170 to the surrounding storage media (e.g., liquid phase
material that is confined within an insulated tank and may produce
a block of solid phase material (ice) surrounding the freezing
coils and storing thermal energy in the process).
[0025] In parallel condenser discharge mode, all basic air
conditioning/refrigerant AC/R components are active including the
compressor 110, condenser 112, evaporator expansion device 120, and
the evaporator 114. In this mode, the compressor 110 is energized
to compress cold, low pressure refrigerant gas to hot,
high-pressure gas. This refrigerant passes through valve V1 122
where a portion of the hot, high-pressure gas is diverted by valve
V1 122 to the storage module 116 and heat exchanger 170, which acts
as a condenser where the hot vapor rejects heat to the storage
media 160, reduces temperature, and condenses. This warm liquid
refrigerant is then sent to the evaporator expansion device 120 via
valve V5 130 where it is mixed with warm liquid refrigerant exiting
the condenser 112 via valve V3 126. The mixed warm liquid
refrigerant is then expanded with the evaporator expansion device
120 and evaporator 114 to provide load cooling/refrigeration and
returns to compressor 110 through valves V6 132 and V7 134 to
complete the refrigeration loop.
[0026] Utilizing the heat exchanger 170 within the storage module
116 in this mode as a condenser, allows a greater amount of
subcooling prior to the expansion process. This is accomplished by
rejecting heat to the cold storage media 160 within the storage
module 116, and improving the effectiveness of the condenser 112 by
reducing the mass flow of refrigerant through condenser 112.
Ultimately, the increased subcooling results in an efficiency
improvement for the system by increasing the refrigeration effect
of the evaporator 114. This increase in efficiency may allow an
increased output by the evaporator 114 thereby effectively
increasing the capacity of the AC/R system during high demand
periods. This may allow a smaller system to be introduced into a
new installation or to increase the capacity of an existing
retrofit system application.
[0027] In the hot vapor desuperheater discharge mode, all basic
AC/R components are active including the compressor 110, condenser
112, evaporator expansion device 120, and the evaporator 114. In
this mode, the compressor 110 is energized to compress cold, low
pressure refrigerant gas to hot, high-pressure gas. This
refrigerant passes through valve V1 122 and is directed to the
previously charged storage module 116 acting as a hot vapor
desuperheater where the hot vapor refrigerant rejects heat to the
storage media 160 via the heat exchanger 170 and reduces
temperature. The vapor is then directed to the condenser 112 via
valve V2 124 where additional atmospheric heat rejection and
condensation occur. The refrigerant leaves the condenser 112 where
the entirety of the subcooled refrigerant is diverted by valve V3
126 to valve V5 130 where refrigerant is then directed to the
evaporator expansion device 120. The warm liquid refrigerant is
expanded and then evaporated in evaporator 114 before being
returned to compressor 110 through valves V6 132 and V7 134.
[0028] In this mode, using the storage module 116, acting as a hot
vapor desuperheater, allows a greater amount of subcooling prior to
the expansion process. This is accomplished by rejecting heat to
the cold storage media 160 within the storage module 116, and
improving the condenser 112 effectiveness by reducing the amount of
heat rejection that must occur in the condenser 112 to desuperheat
the hot vapor refrigerant. Instead, more of the condenser 112 heat
rejection process is used to subcool the warm liquid refrigerant.
Ultimately, the increased subcooling results in an efficiency
improvement for the system by increasing the refrigeration effect
of the evaporator 114. This increase in efficiency may also allow
an increased output by the evaporator 114, thereby effectively
increasing the capacity of the AC/R system during high demand
periods. This may allow a smaller system to be introduced into a
new installation or to increase the capacity of an existing
retrofit system application.
[0029] In the warm liquid subcooler discharge mode, all basic AC/R
components are active including the compressor 110, condenser 112,
evaporator expansion device 120 and the evaporator 114. In this
mode, the compressor 110 is energized to compress cold, low
pressure refrigerant gas to hot, high-pressure gas. This
refrigerant passes through valve V1 122 to a condenser 112, which
removes much of the heat in the gas and discharges the heat to the
atmosphere. The refrigerant leaves the condenser 112 as a warm,
high-pressure liquid refrigerant delivered through a high-pressure
liquid supply line where the entirety of the warm liquid
refrigerant is diverted by valve V3 126 to valve V4 128, which
directs the refrigerant directly to the heat exchanger within the
storage module 116, acting as a warm liquid subcooler, where the
warm liquid refrigerant rejects heat and reduces temperature by
transferring heat to the previously cooled thermal storage media
160.
[0030] The cooled liquid refrigerant is then directed to the
evaporator expansion device 120 via valve V5 130. The subcooled
refrigerant is expanded and then evaporated in evaporator 114
before being returned to compressor 110 through valves V6 132 and
V7 134. In this mode, using the storage module 116 as a warm liquid
subcooler allows a greater amount of subcooling prior to the
expansion process by rejecting heat to the cold storage media 160
within the storage module 116. Ultimately, the increased subcooling
results in an efficiency improvement for the system by increasing
the refrigeration effect of the evaporator 114. This increase in
efficiency may allow an increased output by the evaporator 114,
thereby effectively increasing the capacity of the AC/R system
during high demand periods. This may allow a smaller system to be
introduced into a new installation or to increase the capacity of
an existing retrofit system application.
[0031] In cold vapor desuperheater discharge mode, all basic AC/R
components are active including the compressor 110, condenser 112,
evaporator expansion device 120, and the evaporator 114. In this
mode, the compressor 110 is energized to compress cold, low
pressure refrigerant gas to hot, high-pressure gas. This
refrigerant passes through valve V1 122 to a condenser 112, which
removes much of the heat in the gas and discharges the heat to the
atmosphere. The refrigerant leaves the condenser 112 as a warm,
high-pressure liquid refrigerant delivered through a high-pressure
liquid supply line where the warm liquid refrigerant is diverted by
valve V3 126 to valve V5 130 where refrigerant is then directed to
the evaporator expansion device 120. The refrigerant is expanded
and then evaporated in evaporator 114 in a conventional manner and
the expanded refrigerant is then diverted by valve V6 132 to the
pre-charged storage module 116 acting as a cold vapor desuperheater
where the cold vapor refrigerant rejects heat to the storage media
160 and reduces temperature before being returned to compressor 110
through valve V7 134.
[0032] In this mode, using the storage module 116 as a cold vapor
desuperheater, allows a greater amount of subcooling prior to the
expansion process by rejecting heat to the cold storage media 160
within the storage module 116, and improving the condenser 112
effectiveness by reducing the amount of heat rejection that must
occur in the condenser 112 to desuperheat the hot vapor
refrigerant. Instead, more of the condenser 112 heat rejection
process is used to subcool the warm liquid refrigerant. Ultimately,
the increased subcooling results in an efficiency improvement for
the system by increasing the refrigeration effect of the evaporator
114. This increase in efficiency may allow an increased output by
the evaporator 114 thereby effectively increasing the capacity of
the AC/R system during high demand periods. This may allow a
smaller system to be introduced into a new installation or to
increase the capacity of an existing retrofit system
application.
[0033] In suction line charge mode, all basic AC/R components are
active including the compressor 110, condenser 112, evaporator
expansion device 120, and the evaporator 114. In this mode, the
compressor 110 is energized to compress cold, low pressure
refrigerant gas to hot, high-pressure gas. This refrigerant passes
through valve V1 122 to a condenser 112, which removes much of the
heat in the gas and discharges the heat to the atmosphere. The
refrigerant leaves the condenser 112 as a warm, high-pressure
liquid refrigerant delivered through a high-pressure liquid supply
line where the warm liquid refrigerant is diverted by valve V3 126
to valve V5 130 where refrigerant is then directed to the
evaporator expansion device 120. The refrigerant is expanded and
then evaporated in evaporator 114 in a conventional manner and the
expanded refrigerant is then diverted by valve V6 132 to the
uncharged storage module 116 acting as a cold vapor superheater
where residual cooling that remains in the effluent cold vapor
refrigerant leaving the evaporator 114, is transferred to the
storage media 160, and the temperature of the cold vapor
refrigerant increases. The superheated vapor refrigerant exits the
storage module 116 and returns to compressor 110 through valve V7
134.
[0034] In this mode, using the storage module 116 as a cold vapor
superheater, allows an amount of charging (cooling) of the thermal
storage media 160 prior to compressing the superheated refrigerant.
This places more strain on the compressor 110, but allows an
additional mode of charging the storage module while providing
conventional cooling with the evaporator 114.
[0035] An additional loop may be utilized in the embodiment
described in FIG. 1, which does not utilize TES. A bypass mode 199
may be achieved that acts as a standard AC/R system without
utilization of the storage module 116. In this mode, the compressor
110 is energized to compress cold, low pressure refrigerant gas to
hot, high-pressure gas. This refrigerant passes through valve V1
122 to a condenser 112, which removes much of the heat in the gas
and discharges the heat to the atmosphere. The refrigerant leaves
the condenser 112 as a warm, high-pressure liquid refrigerant
delivered through a high-pressure liquid supply line where the warm
liquid refrigerant is diverted by valve V3 126 to valve V5 130
where refrigerant is then directed to the evaporator expansion
device 120. The refrigerant is expanded and then evaporated in
evaporator 114 in a conventional manner and the expanded
refrigerant is then diverted by valve V6 132 before being returned
to compressor 110 through valve V7 134. In this mode, conventional
AC/R may be utilized in situations where TES is not needed or
desired.
[0036] As illustrated in FIG. 1, a variety of modes may be utilized
in the system shown to provide cooling in various conventional or
non-conventional air conditioning/refrigerant applications. This
system may be a single integrated system with all of the above
disclosed modes present, or the contemplated system may include
various combinations thereof.
[0037] FIG. 2 is a schematic illustration of the valve conditions
for the embodiment of a thermal energy storage refrigerant circuit
capable of multiple charging modes 180 and discharging modes 190
depicted in FIG. 1. As shown in FIG. 2, the valve state conditions
are depicted for each of the seven valves V1 122-V7 134. For
example, in the trickle charge mode, valve V1 122 allows flow from
the compressor to the condenser and is depicted as condition (=).
Valve V2 124 does not allow flow, or is inconsequential with regard
to the flow condition and is depicted with a small box as condition
(.quadrature.). Valve V3 126 allows metered and proportional flow
to both the storage expansion device 118 and the evaporator
expansion device 120 and is depicted as condition (). Thus, each of
the charge mode 180 valve configurations is shown, and in a similar
manner the four discharge modes 190 and a bypass mode 199 are
schematically illustrated.
[0038] FIG. 3 illustrates an AC/R trickle charge loop. In this
particular charging loop, a compressor 110 compresses cold, low
pressure refrigerant gas to hot, high-pressure gas. This
refrigerant passes to a condenser 112, which removes much of the
heat in the gas and discharges the heat to the atmosphere. The
refrigerant leaves the condenser 112 as a warm, high-pressure
liquid refrigerant delivered through a high-pressure liquid supply
line where a portion of the warm liquid refrigerant is diverted by
a valve, which directs the diverted refrigerant through the storage
expansion device 118. The storage expansion device 118 reduces the
pressure of the warm liquid refrigerant to generate a cold
mixed-phase refrigerant. In this loop, the storage module acts as
an evaporator where the cold mixed-phase refrigerant absorbs heat
from the storage media 160 and vaporizes. This storage expansion
device 118 may be a conventional or non-conventional thermal
expansion valve, a static orifice, a capillary tube, a mixed-phase
regulator and surge vessel (reservoir), or the like.
[0039] The liquid refrigerant transfers cooling to thermal energy
storage media 160 within the thermal energy storage module 116
(shown here as a primary heat exchanger 170 within an insulated
tank). Low-pressure vapor phase refrigerant is then returned to the
compressor 110 where it is mixed with the portion of the cold vapor
refrigerant returning to compressor 110 from the evaporator 114
that was split at the valve and passed through an evaporator
expansion device 120. As with the storage expansion device 118,
evaporator expansion device 120 may be a conventional or
non-conventional thermal expansion valve, a static orifice, a
capillary tube, a mixed-phase regulator and surge vessel
(reservoir), or the like.
[0040] As was described in FIG. 1, in order to meter the amount of
refrigerant that is split, a specialized valve may be used to meter
the amount of refrigerant that is diverted to each branch to
provide immediate cooling through evaporator 114, and to the amount
diverted to TES for providing cooling capacity, which may be
utilized at a later time (e.g., a valve and controller that
modulates based on downstream pressures). Alternatively, the
storage media 160 used in the storage module 116 can be selected in
order to match the refrigerant evaporating temperature of the
storage module 116 to that of the evaporator 114, effectively
matching the pressure drop across the storage expansion device 118
and evaporator expansion device 120 and resulting in a
self-metering trickle charge configuration.
[0041] The thermal energy storage unit 116 shown in FIGS. 1 and 3-9
may typically comprise an insulated tank that houses the primary
heat exchanger 170 surrounded by, for example, solid, liquid
coolant, eutectic or liquid phase material and/or solid phase
material or the like, (fluid/ice) depending on the current system
mode). The primary heat exchanger 170 may typically further
comprise a lower header assembly connected to an upper header
assembly with a series of freezing and discharge coils to make a
fluid/vapor loop within the insulated tank. Such systems are
disclosed in the patents and applications referred to above, which
are incorporated by reference.
[0042] FIG. 4 illustrates an AC/R full-capacity charge loop. In
this particular charging loop, the compressor 110 is energized to
compress cold, low pressure refrigerant gas to hot, high-pressure
gas. This refrigerant passes to a condenser 112, which removes much
of the heat in the gas and discharges the heat to the atmosphere.
The refrigerant leaves the condenser 112 as a warm, high-pressure
liquid refrigerant delivered through a high-pressure liquid supply
line where the entirety of the warm liquid refrigerant is directed
to the storage expansion device 118. Here as in the previously
described trickle charge loop, the storage expansion device 118
reduces the pressure of the warm liquid refrigerant to generate a
cold mixed-phase refrigerant. In this mode, the storage module also
acts as an evaporator where the cold mixed-phase refrigerant
absorbs heat from the storage media 160 and vaporizes and transfers
cooling to thermal energy storage media 160 within the thermal
energy storage module 116. Low-pressure vapor phase refrigerant is
then returned to the compressor 110. Thus, the entirety of the
cooling provided by the compressor 110 and condenser 112 (typical
conventional air conditioning or refrigeration unit) is
transmitted, in one contemplated embodiment, from the freezing
coils to the surrounding liquid phase material that is confined
within an insulated tank and may produce a block of solid phase
material (ice) surrounding the freezing coils and storing thermal
energy in the process.
[0043] FIG. 5 illustrates an AC/R parallel condenser discharge
loop. In this particular discharge loop, the compressor 110 is
energized to compress cold, low pressure refrigerant gas to hot,
high-pressure gas. This refrigerant passes through a valve where a
portion of the hot, high-pressure gas is diverted to the storage
module 116, which acts as a condenser where the hot vapor rejects
heat to the storage media 160, reduces temperature, and condenses.
This warm liquid refrigerant is then sent to the evaporator
expansion device 120 where it is mixed with warm liquid refrigerant
exiting the condenser 112. The mixed warm liquid refrigerant is
then expanded with the evaporator expansion device 120 and
evaporator 114 to provide load cooling/refrigeration and returns to
compressor 110 to complete the refrigeration loop.
[0044] FIG. 6 illustrates an AC/R hot vapor desuperheater discharge
loop. In this particular discharge loop, the compressor 110 is
energized to compress cold, low pressure refrigerant gas to hot,
high-pressure gas. This refrigerant is directed to the previously
charged storage module 116 acting as a hot vapor desuperheater
where the hot vapor refrigerant rejects heat to the storage media
160 and reduces temperature. The vapor is then directed to the
condenser 112, where additional atmospheric heat rejection and
condensation occur. The refrigerant leaves the condenser 112, where
the entirety of the desuperheated refrigerant is directed to the
evaporator expansion device 120. The warm liquid refrigerant is
expanded and then evaporated in evaporator 114 before being
returned to compressor 110.
[0045] FIG. 7 illustrates an AC/R warm liquid subcooler discharge
loop. In this particular discharge loop, the compressor 110 is
energized to compress cold, low pressure refrigerant gas to hot,
high-pressure gas. This refrigerant passes to a condenser 112,
which removes much of the heat in the gas and discharges the heat
to the atmosphere. The refrigerant leaves the condenser 112 as a
warm, high-pressure liquid refrigerant delivered through a
high-pressure liquid supply line where the entirety of the warm
liquid refrigerant is directed to the storage module 116, which
acts as a warm liquid subcooler where the warm liquid refrigerant
rejects heat to the storage media 160 and reduces temperature by
transferring heat to the previously cooled thermal storage media
160. The cooled liquid refrigerant is then directed to the
evaporator expansion device 120. The subcooled refrigerant is
expanded and then evaporated in evaporator 114 before being
returned to compressor 110.
[0046] FIG. 8 illustrates an AC/R cold vapor desuperheater
discharge loop. In this particular discharge loop, the compressor
110 is energized to compress cold, low pressure refrigerant gas to
hot, high-pressure gas. This refrigerant passes to a condenser 112,
which removes much of the heat in the gas and discharges the heat
to the atmosphere. The refrigerant leaves the condenser 112 as a
warm, high-pressure liquid refrigerant delivered through a
high-pressure liquid supply line where the warm liquid refrigerant
is then directed to the evaporator expansion device 120. The
refrigerant is expanded and then evaporated in evaporator 114 in a
conventional manner and the expanded refrigerant is then diverted
to the pre-charged storage module 116, acting as a cold vapor
desuperheater where the cold vapor refrigerant rejects heat to the
storage media 160 and reduces temperature before being returned to
compressor 110.
[0047] FIG. 9 illustrates an AC/R suction line charge loop. In this
particular charging loop, the configuration of the loop is the same
as the cold vapor desuperheater discharge loop illustrated in FIG.
8, except that the storage module 116 is being charged instead of
being discharged. In this loop, the compressor 110 is energized to
compress cold, low pressure refrigerant gas to hot, high-pressure
gas. This refrigerant passes to a condenser 112, which removes much
of the heat in the gas and discharges the heat to the atmosphere.
The refrigerant leaves the condenser 112 as a warm, high-pressure
liquid refrigerant delivered through a high-pressure liquid supply
line where the warm liquid refrigerant is diverted by valve V3 126
through valve V5 130 to the evaporator expansion device 120. The
evaporator expansion device 120 reduces the pressure of the warm
liquid refrigerant to generate a cold mixed-phase refrigerant. In
this mode, the evaporator 114 provides cooling as during typical
AC/R operation. The cold vapor refrigerant exits the evaporator 114
and is diverted by valve V6 132 to the storage module 116 where
residual cooling that remains in the effluent refrigerant leaving
the evaporator 114 is transferred to the storage media 160, and the
temperature of the cold vapor refrigerant increases. The
superheated vapor refrigerant exits the storage module 116 and
returns to compressor 110.
[0048] The disclosed system may utilize a relatively small capacity
condenser compressor (air conditioner) and have the ability to
deliver high capacity cooling utilizing thermal energy storage.
This variability may be further extended by specific sizing of the
compressor and condenser components within the system. Whereas the
aforementioned refrigerant loops have been described as having a
particular direction, it is shown and contemplated that these loops
may be run in either direction whenever possible.
[0049] The foregoing description of the invention has been
presented for purposes of illustration and description. It is not
intended to be exhaustive or to limit the invention to the precise
form disclosed, and other modifications and variations may be
possible in light of the above teachings. The embodiment was chosen
and described in order to best explain the principles of the
invention and its practical application to thereby enable others
skilled in the art to best utilize the invention in various
embodiments and various modifications as are suited to the
particular use contemplated. It is intended that the appended
claims be construed to include other alternative embodiments of the
invention except insofar as limited by the prior art.
* * * * *