U.S. patent application number 13/317798 was filed with the patent office on 2013-05-02 for mass flow multiplier refrigeration cycle.
The applicant listed for this patent is Gasper C. Occhipinti. Invention is credited to Gasper C. Occhipinti.
Application Number | 20130104593 13/317798 |
Document ID | / |
Family ID | 48170989 |
Filed Date | 2013-05-02 |
United States Patent
Application |
20130104593 |
Kind Code |
A1 |
Occhipinti; Gasper C. |
May 2, 2013 |
Mass flow multiplier refrigeration cycle
Abstract
The ejector mass flow multiplier refrigeration cycle utilizes a
single-phase ejector which is operated at a high entrainment ratio
and performs the function as a mass flow multiplier. The
high-pressure motive force input into the single-phase ejector is
provided by a vapor compressor which sucks a portion of the output
mass flow from an evaporator with the remaining mass flow output
from the evaporator being sucked into low-pressure port of the same
single-phase ejector. The low-pressure output of the single-phase
ejector is inputted into the low-pressure port of a two-phase
ejector where the mass flow pressure is increased for the
temperature conditions of a condenser. A high-pressure liquid pump
provides the motive force input of the two-phase ejector and for
the input to an evaporator where the cooling effect of the system
takes place.
Inventors: |
Occhipinti; Gasper C.;
(Covington, LA) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Occhipinti; Gasper C. |
Covington |
LA |
US |
|
|
Family ID: |
48170989 |
Appl. No.: |
13/317798 |
Filed: |
October 28, 2011 |
Current U.S.
Class: |
62/498 |
Current CPC
Class: |
F25B 41/00 20130101;
F25B 2341/0015 20130101; F25B 2341/0014 20130101; F25B 5/02
20130101 |
Class at
Publication: |
62/498 |
International
Class: |
F25B 1/00 20060101
F25B001/00 |
Claims
1. A mass flow multiplier refrigeration cycle comprising: a vapor
compressor for sucking and converting a low-pressure vapor
refrigerant into a high-pressure vapor refrigerant. The vapor
compressor capacity is a fraction of the overall system
refrigeration output; an evaporator(s) for evaporating a
low-pressure refrigerant after being decompressed in which heat is
absorbed; an expansion valve(s) for decompressing a high-pressure
liquid refrigerant into a low-pressure refrigerant for input into
an evaporator; a condenser for converting a high-pressure vapor
refrigerant into a high-pressure liquid refrigerant by the removal
of heat; a high pressure liquid pump which increases the liquid
refrigerant into a higher pressure whose mass flow is a multiple of
the systems rated capability; a single-phase ejector whose
operating parameters are such that the ER (entrainment ratio) is
maximized; a two-phase ejector whose operating parameters are such
that the output pressure is increased for the temperature
conditions of a condenser.
Description
BACKGROUND OF THE INVENTION
[0001] 1. Field of the Invention
[0002] The present invention relates to a refrigeration system,
which utilizes an evaporator(s), condenser, vapor compressor,
single-phase ejector, two-phase ejector and a liquid pressure
pump.
[0003] 2. Description of the Prior Art
[0004] The vapor compression refrigeration cycle is the predominate
cooling method for millions of residential and commercial
installations. The vapor compression cycle utilizes a vapor
compressor to increase a low-pressure refrigerant gas to a
high-pressure refrigerant gas. The high-pressure gas then passes
through an air or water-cooled condenser where the gas changes
state into a high-pressure, liquid upon the removal of heat from
the high-pressure gas. This high-pressure liquid then passes
through an expansion valve into an evaporator. During this
expansion process, heat is absorbed in the evaporator with space
air or other medium being circulated through the evaporator. The
net result is the cooling of the conditioned space or medium.
[0005] A further improvement to the above vapor compression
refrigeration cycle is a vapor-compression refrigeration cycle with
ejector as shown in FIG. 1. This ejector cycle described in U.S.
Pat. No. 6,438,993, reduces the amount of work or energy input
required by the vapor compressor. High-pressure refrigerant is
decompressed and expanded in a nozzle of an ejector with the
liquid-phase refrigerant separated in a gas-liquid separator is
supplied to an evaporator by the pumping function of the ejector.
Further, in the above ejector cycle, a pressure of refrigerant to
be sucked into a compressor is increased by converting expansion
energy to Pressure energy, so that consumption power of the vapor
compressor is reduced.
SUMMARY
[0006] The present invention consists of a vapor compressor which
is rated at a fraction of the overall system cooling capability.
The vapor compressor at its rated flow capacity sucks a portion of
the low-pressure gas output from an evaporator and compresses the
vapor into a high pressure gas which provides the primary motive
force input flow into a single-phase ejector. Concurrently, the
remaining low pressure volume output from the evaporator passes
into the low-pressure input port of the same single-phase ejector.
The purpose of this single-phase ejector is not to increase the
pressure output but to produce a high entrainment or sucking ratio
(ER) which performs as a system mass flow multiplier. Reference is
made to "A Dissertation by Chaqing Liao" entitled "GAS EJECTOR
MODELING FOR DESIGN AND ANALYSIS", Office of Graduate Studies of
Texas A&M University. This document outlines the design
parameters for a single-phase ejector with a high ER.
[0007] The output of the above single-phase ejector is inputted
into the low pressure input port of a two-phase ejector whose
purpose is to increase the output pressure necessary for the
temperature conditions of the condenser. The motive force input
into the two-phase ejector is provided by a high-pressure liquid
pump. The pressure enhancement capabilities of a typical two-phase
ejector are more fully described in an early U.S. Pat. No.
3,277,660 and most recently refined in U.S. Pat. No. 6,438,993. The
high-pressure vapor output of the two-phase ejector is inputted
into a condenser where a phase change into a high-pressure liquid
pressure is accomplished.
[0008] The high-pressure liquid from the condenser proceeds into a
high-pressure liquid pump where the liquid pressure is further
increased. Upon leaving the liquid pressure pump, the output is
divided into two liquid streams. The first stream is directed into
the driving motive force input port of the two-phase ejector, while
the second stream is directed into the expansion valve then into
the evaporator. During this expansion process, heat is absorbed in
the evaporator with space air or other medium being circulated
through the evaporator. The net result is the cooling of the
conditioned space or medium.
[0009] The net refrigeration output of this cycle is a function of
the mass flow of the vapor compressor plus the ER of the
single-phase ejector times the mass flow of the vapor
compressor.
[0010] It is an object of the invention to provide a simple
refrigeration system with significant advantages over the vapor
compressor system widely in use today.
[0011] Additional objects and advantages of the invention are set
forth, in part in the description which follows, and in part, will
be obvious from description or may learned by practice of the
invention. The objects and advantages of the invention will be
realized in detail by means of the instrumentalities and
combinations particularly pointed out in the appended claim.
BRIEF DESCRIPTION OF THE DRAWINGS
[0012] Additional objects and advantages of the invention will be
more readily apparent from the following detailed description of
the preferred embodiment, when taken together with the accompanying
drawings, in which:
[0013] FIG. 1 is a schematic diagram showing an ejector cycle
(vapor-compression refrigerant cycle) according to U.S. Pat. No.
6,438,993;
[0014] FIG. 2 is a schematic diagram showing a mass flow multiplier
refrigeration cycle used in the present invention;
[0015] FIG. 3 is a schematic diagram showing a mass flow multiplier
refrigeration cycle with the addition of a second evaporator.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
[0016] It is understood that both the foregoing general description
and following detailed description are exemplary and explanatory
only, and are not restrictive of the invention as claimed. The
accompanying drawings as shown in FIG. 2 and FIG. 3 which are
incorporated herein for reference, and constitute part of the
specifications, illustrate certain embodiments of the invention,
and together with the detailed description serve to explain the
principles of the present invention.
[0017] As shown in FIG. 2 the refrigeration cycle of the present
invention utilizes a typical refrigerant such as R134a and begins
with a portion of the low pressure vapor output from evaporator 23
proceeding through conduits 24 and 25 and is sucked into the vapor
compressor 10 where the vapor is increased from a low to a
high-pressure output.
[0018] This high-pressure vapor refrigerant proceeds through
conduit 11 into the driving motive force input port 12a of a
single-phase ejector 12 (ejector 12). The motive force flow is
accelerated to supersonic speed by a converging-diverging nozzle.
The primary flow exit in the ejector suction chamber induces a
secondary flow by this high-velocity depressurized flow.
Concurrently the remaining portion of the low-pressure gas output
from evaporator 23 proceeds through conduits 24 and 26 into the low
pressure port 12b of ejector 12. This is accomplished by the
sucking or entrainment capabilities of ejector 12. The ejector 12
operating parameters are set such that the entrainment ratio (ER)
is maximized. This requires that the output at port 12c works
against a low back pressure.
[0019] The low-pressure output from port 12c of ejector 12 is
directed into the low-pressure suction port of a two-phase ejector
14 (ejector 14) via conduit 13. Concurrently a high-pressure liquid
stream from a high-pressure liquid pump 17 flows through conduits
16 and 15 into the driving motive force input port 14a of ejector
14. It is to be noted that the horsepower to pressurize a liquid
for a given mass flow of refrigerant by a positive displacement
pressure pump is significantly less than the horsepower required
for a vapor compression cycle of equal mass flow. The input into
port 14a of ejector 14 decompresses and mixes with the low-pressure
gas output from ejector 12. The ejector 14 performs two functions,
the first being the entrainment or sucking of low-pressure vapor
from ejector 12 into the low-pressure input port 14b. The second
function is the conversion of speed energy into pressure energy
enhancement which is required for the temperature conditions of
condenser 19.
[0020] The pressure enhancement capabilities of a typical two-phase
ejector are more fully described in an early U.S. Pat. No.
3,277,660 and most recently described in U.S. Pat. No. 6,438,993.
Upon leaving port 14c of ejector 14, the refrigerant travels
through conduit 20 and enters condenser 19 where heat is removed
thereby condensing the refrigerant into a high-pressure liquid.
This high-pressure liquid proceeds through conduit 18 into a
high-pressure liquid pump 17 where the liquid pressure is further
increased. Upon leaving the liquid pressure pump 17, the
high-pressure liquid passes through conduit 16 where the flow is
divided into two liquid streams. The first stream is directed
through conduit 15 into the driving motive force input port 14a of
ejector 14, while the second stream is directed through conduit 21
entering the expansion valve 22 then into evaporator 23. The
expansion valve 22 opens and closes depending upon the set point
temperature requirements of the evaporator 23. There are several
schemes to accomplish this control function currently in use today.
During this expansion process the refrigerant undergoes a phase
change whereby heat is absorbed in the evaporator 23 with space air
or other medium being circulated through evaporators 23. The net
result is the cooling of the conditioned space or medium.
[0021] Again a portion of the low-pressure output of evaporator 23
travels through conduits 24 and 25 into the vapor compressor 10.
Concurrently, the remaining output of evaporator 23 travels through
conduits 24 and 26 into the low-pressure port 12b of the ejector
12. This final step completes the cycle where it is then
repeated.
[0022] It is to be noted that an alternate variation to the above
cycle is shown in FIG. 3 where a second evaporator 23A is added.
Beginning with conduit 21 the liquid stream is divided whereby the
majority of the mass flow proceeds through conduit 21A into
expansion valve 22A then into evaporator 23A. The low-pressure
output from evaporator 23A proceeds through conduits 26A and 26
into the low-pressure input port 12b of ejector 12.
[0023] It will be apparent to those skilled in the art that various
modifications can be made in the construction and configuration of
the present invention without departing from the scope or spirit of
the invention. For example, the embodiment mentioned above is
illustrative and explanatory only. Various changes can be made in
material as well as the configuration of the device to engineer the
specific desired outcome. Thus it is intended that the present
invention cover the modifications and variations of the invention,
provided they come within the scope of the appended claims and
their equivalents.
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