U.S. patent application number 13/981637 was filed with the patent office on 2014-06-12 for ejector.
This patent application is currently assigned to CARRIER CORPORATION. The applicant listed for this patent is Frederick J. Cogswell, Parmesh Verma, Jinliang Wang. Invention is credited to Frederick J. Cogswell, Parmesh Verma, Jinliang Wang.
Application Number | 20140157807 13/981637 |
Document ID | / |
Family ID | 45349328 |
Filed Date | 2014-06-12 |
United States Patent
Application |
20140157807 |
Kind Code |
A1 |
Cogswell; Frederick J. ; et
al. |
June 12, 2014 |
Ejector
Abstract
An ejector (200; 300; 400; 600) has a primary inlet (40), a
secondary inlet (42), and an outlet (44). A primary flowpath
extends from the primary inlet to the outlet. A secondary flowpath
extends from the secondary inlet to the outlet. A mixer convergent
section (114) is downstream of the secondary inlet. A motive nozzle
(100) surrounds the primary flowpath upstream of a junction with
the secondary flowpath. The motive nozzle has an exit (110). A
secondary inlet passageway along the secondary flowpath has a
terminal portion oriented to discharge a secondary flow along the
secondary flowpath at an angle of less than 75.degree. off-parallel
to a local direction of the primary flowpath.
Inventors: |
Cogswell; Frederick J.;
(Glastonbury, CT) ; Wang; Jinliang; (Ellington,
CT) ; Verma; Parmesh; (Manchester, CT) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Cogswell; Frederick J.
Wang; Jinliang
Verma; Parmesh |
Glastonbury
Ellington
Manchester |
CT
CT
CT |
US
US
US |
|
|
Assignee: |
CARRIER CORPORATION
Farmington
CT
|
Family ID: |
45349328 |
Appl. No.: |
13/981637 |
Filed: |
December 8, 2011 |
PCT Filed: |
December 8, 2011 |
PCT NO: |
PCT/US11/63920 |
371 Date: |
July 25, 2013 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
61445788 |
Feb 23, 2011 |
|
|
|
61446901 |
Feb 25, 2011 |
|
|
|
Current U.S.
Class: |
62/115 ; 239/408;
62/498 |
Current CPC
Class: |
F25B 2341/0011 20130101;
F25B 2500/01 20130101; F25B 41/00 20130101 |
Class at
Publication: |
62/115 ; 239/408;
62/498 |
International
Class: |
F25B 41/00 20060101
F25B041/00 |
Claims
1. An ejector (200; 300; 400; 600) comprising: a primary inlet
(40); a secondary inlet (42); an outlet (44); a primary flowpath
from the primary inlet to the outlet; a secondary flowpath from the
secondary inlet to the outlet; a mixer convergent section (114)
downstream of the secondary inlet; and a motive nozzle (222)
surrounding the primary flowpath upstream of a junction with the
secondary flowpath and having an exit (110); wherein: a secondary
inlet passageway (218; 218A, 218B; 218'A, 218'B; 218''A, 218''B)
has a terminal portion oriented to discharge a secondary flow along
the secondary flowpath at an angle (.theta.) of 10-75.degree.
off-parallel to a local direction of the primary flowpath; and a
center of an outlet of the terminal portion is at a radius
(R.sub.1) from an axis (500) of the motive nozzle and axially
recessed by a distance (L.sub.1) relative to the exit (110) of the
motive nozzle.
2. The ejector (200; 300; 600) of claim 1 wherein: the motive
nozzle is mounted in a first bore; and the secondary inlet
passageway is at least partially defined by a fitting mounted in a
second bore.
3. The ejector (600) of claim 2 wherein: the fitting protrudes into
a chamber (232) surrounding the motive nozzle.
4. The ejector of claim 2 wherein: the second bore is 30-60.degree.
off perpendicular to the first bore.
5. The ejector of claim 1 wherein: L.sub.1 is less than 40 mm and
R.sub.1 is less than 45 mm.
6. The ejector of claim 1 wherein: said angle is 35-55.degree..
7. The ejector (300; 400; 600) of claim 1 wherein: there are at
least two said secondary inlet passageways (218A, 218B; 218'A,
218'B; 218''A, 218''B).
8. The ejector of claim 1 further comprising: a needle (132)
mounted for reciprocal movement along the primary flowpath between
a first position and a second position; and a needle actuator (134)
coupled to the needle to drive said movement of the needle relative
to the motive nozzle.
9. The ejector of claim 1 wherein: an outer member comprises an
end-to-end axial assembly of a plurality of sections.
10. The ejector of claim 9 wherein the sections include: an
upstream section (202) at least partially surrounding the motive
nozzle; one or more intermediate sections (204) at least partially
defining a convergent portion (214) and a mixing portion (216); and
at least one downstream section (206) at least partially defining a
divergent portion (118).
11. The ejector of claim 10 wherein: an interface of at least two
of said sections (204, 206) comprises a boss of one section
protruding into a compartment in the other section.
12. A vapor compression system comprising: a compressor (22); a
heat rejection heat exchanger (30) coupled to the compressor to
receive refrigerant compressed by the compressor; the ejector (200;
300; 400; 600) of claim 1; a heat absorption heat exchanger (64);
and a separator (48) having: an inlet (50) coupled to the outlet of
the ejector to receive refrigerant from the ejector; a gas outlet
(54); and a liquid outlet (52).
13. A method for operating the system of claim 12 comprising:
compressing the refrigerant in the compressor; rejecting heat from
the compressed refrigerant in the heat rejection heat exchanger;
passing a flow of the refrigerant through the primary ejector
inlet; and passing a secondary flow of the refrigerant through the
secondary inlet to merge with the primary flow.
14. The method of claim 13 wherein: the refrigerant comprises at
least 50% CO.sub.2 by weight.
15. An ejector comprising: a primary inlet (40); a secondary inlet
(42); an outlet (44); a primary flowpath from the primary inlet to
the outlet; a secondary flowpath from the secondary inlet to the
outlet; a convergent section (114) downstream of the secondary
inlet; a motive nozzle (222) surrounding the primary flowpath
upstream of a junction with the secondary flowpath and having: a
throat (106); and an exit (110); and means for efficiently
promoting mixing of the secondary flow into the primary flow.
16. The ejector of claim 15 wherein: the means comprises an
off-radially directed terminal portion of of a secondary passageway
from the secondary inlet.
17. The ejector of claim 15 wherein: a center of an outlet of the
terminal portion is at a radius (R.sub.1) from an axis (500) of the
motive nozzle and axially recessed by a distance (L.sub.1) relative
to the exit (110) of the motive nozzle.
18. The ejector of claim 17 wherein: L.sub.1 is at least 5 mm.
19. The ejector of claim 1 wherein: an axis of an outlet of the
terminal portion intersects an axis of the motive nozzle at a
location upstream of the exit of the motive nozzle.
20. The ejector of claim 1 wherein: L.sub.1 is at least 5 mm.
Description
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] Benefit is claimed of U.S. Patent Application Ser. No.
61/445,788, filed Feb. 23, 2011, and entitled "Ejector" and U.S.
Patent Application Ser. No. 61/446,901, filed Feb. 25, 2011, and
entitled "Ejector", the disclosures of which are incorporated by
reference herein in their entireties as if set forth at length.
BACKGROUND
[0002] The present disclosure relates to refrigeration. More
particularly, it relates to ejector refrigeration systems.
[0003] Earlier proposals for ejector refrigeration systems are
found in U.S. Pat. No. 1,836,318 and U.S. Pat. No. 3,277,660. FIG.
1 shows one basic example of an ejector refrigeration system 20.
The system includes a compressor 22 having an inlet (suction port)
24 and an outlet (discharge port) 26. The compressor and other
system components are positioned along a refrigerant circuit or
flowpath 27 and connected via various conduits (lines). A discharge
line 28 extends from the outlet 26 to the inlet 32 of a heat
exchanger (a heat rejection heat exchanger in a normal mode of
system operation (e.g., a condenser or gas cooler)) 30. A line 36
extends from the outlet 34 of the heat rejection heat exchanger 30
to a primary inlet (liquid or supercritical or two-phase inlet) 40
of an ejector 38. The ejector 38 also has a secondary inlet
(saturated or superheated vapor or two-phase inlet) 42 and an
outlet 44. A line 46 extends from the ejector outlet 44 to an inlet
50 of a separator 48. The separator has a liquid outlet 52 and a
gas outlet 54. A suction line 56 extends from the gas outlet 54 to
the compressor suction port 24. The lines 28, 36, 46, 56, and
components therebetween define a primary loop 60 of the refrigerant
circuit 27. A secondary loop 62 of the refrigerant circuit 27
includes a heat exchanger 64 (in a normal operational mode being a
heat absorption heat exchanger (e.g., evaporator)). The evaporator
64 includes an inlet 66 and an outlet 68 along the secondary loop
62 and expansion device 70 is positioned in a line 72 which extends
between the separator liquid outlet 52 and the evaporator inlet 66.
An ejector secondary inlet line 74 extends from the evaporator
outlet 68 to the ejector secondary inlet 42.
[0004] In the normal mode of operation, gaseous refrigerant is
drawn by the compressor 22 through the suction line 56 and inlet 24
and compressed and discharged from the discharge port 26 into the
discharge line 28. In the heat rejection heat exchanger, the
refrigerant loses/rejects heat to a heat transfer fluid (e.g.,
fan-forced air or water or other fluid). Cooled refrigerant exits
the heat rejection heat exchanger via the outlet 34 and enters the
ejector primary inlet 40 via the line 36.
[0005] The exemplary ejector 38 (FIG. 2) is formed as the
combination of a motive (primary) nozzle 100 nested within an outer
member 102. The primary inlet 40 is the inlet to the motive nozzle
100. The outlet 44 is the outlet of the outer member 102. The
primary refrigerant flow 103 enters the inlet 40 and then passes
into a convergent section 104 of the motive nozzle 100. It then
passes through a throat section 106 and an expansion (divergent)
section 108 through an outlet (exit) 110 of the motive nozzle 100.
The motive nozzle 100 accelerates the flow 103 and decreases the
pressure of the flow. The secondary inlet 42 forms an inlet of the
outer member 102. The pressure reduction caused to the primary flow
by the motive nozzle helps draw the secondary flow 112 into the
outer member. The outer member includes a mixer having a convergent
section 114 and an elongate throat or mixing section 116. The outer
member also has a divergent section or diffuser 118 downstream of
the elongate throat or mixing section 116. The motive nozzle outlet
110 is positioned within the convergent section 114. As the flow
103 exits the outlet 110, it begins to mix with the flow 112 with
further mixing occurring through the mixing section 116 which
provides a mixing zone. Thus, respective primary and secondary
flowpaths extend from the primary inlet and secondary inlet to the
outlet, merging at the exit. In operation, the primary flow 103 may
typically be supercritical upon entering the ejector and
subcritical upon exiting the motive nozzle. The secondary flow 112
is gaseous (or a mixture of gas with a smaller amount of liquid)
upon entering the secondary inlet port 42. The resulting combined
flow 120 is a liquid/vapor mixture and decelerates and recovers
pressure in the diffuser 118 while remaining a mixture. Upon
entering the separator, the flow 120 is separated back into the
flows 103 and 112. The flow 103 passes as a gas through the
compressor suction line as discussed above. The flow 112 passes as
a liquid to the expansion valve 70. The flow 112 may be expanded by
the valve 70 (e.g., to a low quality (two-phase with small amount
of vapor)) and passed to the evaporator 64. Within the evaporator
64, the refrigerant absorbs heat from a heat transfer fluid (e.g.,
from a fan-forced air flow or water or other liquid) and is
discharged from the outlet 68 to the line 74 as the aforementioned
gas.
[0006] Use of an ejector serves to recover pressure/work. Work
recovered from the expansion process is used to compress the
gaseous refrigerant prior to entering the compressor. Accordingly,
the pressure ratio of the compressor (and thus the power
consumption) may be reduced for a given desired evaporator
pressure. The quality of refrigerant entering the evaporator may
also be reduced. Thus, the refrigeration effect per unit mass flow
may be increased (relative to the non-ejector system). The
distribution of fluid entering the evaporator is improved (thereby
improving evaporator performance). Because the evaporator does not
directly feed the compressor, the evaporator is not required to
produce superheated refrigerant outflow. The use of an ejector
cycle may thus allow reduction or elimination of the superheated
zone of the evaporator. This may allow the evaporator to operate in
a two-phase state which provides a higher heat transfer performance
(e.g., facilitating reduction in the evaporator size for a given
capability).
[0007] The exemplary ejector may be a fixed geometry ejector or may
be a controllable ejector. FIG. 2 shows controllability provided by
a needle valve 130 having a needle 132 and an actuator 134. The
actuator 134 shifts a tip portion 136 of the needle into and out of
the throat section 106 of the motive nozzle 100 to modulate flow
through the motive nozzle and, in turn, the ejector overall.
Exemplary actuators 134 are electric (e.g., solenoid or the like).
The actuator 134 may be coupled to and controlled by a controller
140 which may receive user inputs from an input device 142 (e.g.,
switches, keyboard, or the like) and sensors (not shown). The
controller 140 may be coupled to the actuator and other
controllable system components (e.g., valves, the compressor motor,
and the like) via control lines 144 (e.g., hardwired or wireless
communication paths). The controller may include one or more:
processors; memory (e.g., for storing program information for
execution by the processor to perform the operational methods and
for storing data used or generated by the program(s)); and hardware
interface devices (e.g., ports) for interfacing with input/output
devices and controllable system components.
SUMMARY
[0008] One aspect of the disclosure involves an ejector having a
primary inlet, a secondary inlet, and an outlet. A primary flowpath
extends from the primary inlet to the outlet. A secondary flowpath
extends from the secondary inlet to the outlet. A mixer convergent
section is downstream of the secondary inlet. A motive nozzle
surrounds the primary flowpath upstream of a junction with the
secondary flowpath. The motive nozzle has an exit. A secondary
inlet passageway along the secondary flowpath has a terminal
portion oriented to discharge a secondary flow along the secondary
flowpath at an angle of less than 75.degree. off-parallel to a
local direction of the primary flowpath.
[0009] In various implementations, the motive nozzle may be mounted
in a first bore. The secondary inlet passageway may be at least
partially defined by a fitting mounted in a second bore. The second
bore may be 30-60.degree. off-perpendicular to the first bore.
There may be at least two such secondary inlet passageways. A
needle may be mounted for reciprocal movement along the primary
flowpath between a first position and a second position. A needle
actuator may be coupled to the needle to drive the movement of the
needle relative to the motive nozzle.
[0010] Other aspects of the disclosure involve a refrigeration
system having a compressor, a heat rejection heat exchanger coupled
to the compressor to receive refrigerant compressed by the
compressor, a heat absorption heat exchanger, a separator, and such
an ejector. An inlet of the separator may be coupled to the outlet
of the ejector to receive refrigerant from the ejector.
[0011] The details of one or more embodiments are set forth in the
accompanying drawings and the description below. Other features,
objects, and advantages will be apparent from the description and
drawings, and from the claims.
BRIEF DESCRIPTION OF THE DRAWINGS
[0012] FIG. 1 is a schematic view of a prior art ejector
refrigeration system.
[0013] FIG. 2 is an axial sectional view of a prior art
ejector.
[0014] FIG. 3 is a schematic axial sectional view of an
ejector.
[0015] FIG. 3A is an enlarged view of a motive nozzle chamber area
of the ejector of FIG. 3.
[0016] FIG. 4 is a schematic axial sectional view of a second
ejector.
[0017] FIG. 5 is a schematic axial sectional view of a third
ejector.
[0018] FIG. 6 is a schematic axial sectional view of a fourth
ejector.
[0019] Like reference numbers and designations in the various
drawings indicate like elements.
DETAILED DESCRIPTION
[0020] FIG. 3 shows an ejector 200. The ejector 200 may be formed
as a modification of the ejector 38 and may be used in vapor
compression systems (e.g., FIG. 1) where conventional ejectors are
presently used or may be used in the future. An exemplary ejector
is a two-phase ejector used with CO.sub.2 refrigerant (e.g., at
least 50% CO.sub.2 by weight).
[0021] The exemplary ejector includes a multi-part body assembly
(e.g., formed of aluminum, stainless steel, or other machinings).
The body parts 202, 204, 206 are axially secured to each other via
screws, bolts, or other fasteners 208 and may have appropriate
seals 210 (e.g., polymer-o-rings) and the like.
[0022] A secondary flow conduit 216 extends from the secondary
inlet 42 to a conduit outlet 217 and defines a secondary passageway
218. The terminal portion of the secondary passageway is oriented
to discharge the secondary flow off-normal to an axis of the motive
nozzle.
[0023] An exemplary upstream body section 202 has a central axial
bore 220 to which the motive nozzle (or assembly) 222 is mounted.
For ease of reference, similar reference numerals will be used for
the portion of the motive nozzle 222 as for the prior art nozzle.
Similarly, similar reference numerals are used for portions of the
outer member (formed by the body portion 202, 204, 206) as are used
for the outer member 102. The upstream body section 202 further has
a stepped secondary bore 224 to which a secondary inlet fitting 226
(e.g., a conventional stainless steel threaded fitting) is mounted
(e.g., via threaded engagement). A downstream end 227 of the
exemplary fitting lies within the secondary bore. An upstream end
228 of the secondary inlet fitting may define the secondary inlet
42 of the ejector. A terminal portion 230 of the secondary bore
intersects an annular chamber 232 surrounding the motive nozzle. In
the exemplary configuration, the terminal portion 230 of the
secondary bore defines a terminal portion of the secondary inlet
passageway. The terminal portion is oriented coaxial with the
fitting along a secondary axis 502. Along the terminal portion, the
axis 502 is essentially coincident with the direction and centroid
of the secondary flow being discharged into the chamber 232.
[0024] The exemplary terminal portion is oriented to discharge the
secondary flow essentially parallel to the secondary axis at an
angle .theta. off-parallel to the centerline 500 of the motive flow
and associated motive nozzle axis. An exemplary .theta. is
10-75.degree., more narrowly, 30-60.degree., 35-55.degree. or
40-50.degree. or a narrowest 43-45.degree.. By reducing .theta.
relative to the prior art 90.degree., momentum and mixing losses
are reduced and pressure recovery improved. Thus, exemplary .theta.
is less than 75.degree., more narrowly, less than 60.degree..
However, it may be desirable to impose a minimum value on .theta..
If .theta. is too low, the length of nozzle required for adequate
mixing of the primary and secondary flows may be too great.
Accordingly, exemplary minimum values of .theta. are 10.degree.,
more narrowly, 15.degree. or 30.degree.. As is discussed below, a
downstream tapering of the adjacent portion of the outer surface of
the motive nozzle may further smooth flow and reduce losses.
[0025] FIG. 3A shows the effective center of the secondary
passageway as the intersection 518 of the centerline/axis 502 with
the former outer wall 233 (or projection 520 thereof) which was
penetrated by the stepped bore. The local radius at this location
518 relative to the ejector and motive nozzle axis 500 is shown as
R.sub.1. An axial length between this location 518 and the outlet
of the motive nozzle is shown as L.sub.1. In some possible
embodiments, the outlet/exit of the motive nozzle may be coincident
with its throat. In an exemplary ejector, exemplary R.sub.1 is
0.25-100 mm, more narrowly, 1-75 mm or 5-45 mm. Exemplary L.sub.1
is 0-100 mm, more narrowly, 3-60 mm or 5-40 mm. An exemplary axis
502 intersects axis 500 at a location between 2.0R.sub.1 upstream
of the motive nozzle exit and 1.0R.sub.1 downstream, more narrowly,
between 1.0R.sub.1 upstream and 0.5R.sub.1 downstream, and, more
narrowly, between 0.5R.sub.1 upstream and the exit itself.
[0026] The radial velocity component (at the location of initial
mixing proximate the exit 110) of the relatively low velocity
ejector suction flow is relevant to optimizing the losses
associated with mixing of very high velocity ejector motive flow.
If there is no radial velocity component, then the two flows take
longer to mix and losses associated with friction increases. If the
radial velocity is too large, as compared to the tangential
velocity, then mixing occurs fast but losses associated with
viscous dissipation increase. There is an optimal radial velocity
that minimizes the two losses while maximizing mixing.
[0027] The cross-sectional area of the annular flow channel formed
along the chamber 232 and mixer 114 upstream of the exit 110 of the
motive nozzle largely influences the overall velocity of the
secondary (suction) flow. The angles of convergence of the adjacent
surfaces then help define the radial velocity relative to axial
velocity. A half angle range of 2.5-20.degree. (more narrowly
5-15.degree. or)8-12.degree. for both: the motive nozzle outer
surface portion 258 near the motive nozzle exit 110
(.theta..sub.2); and the mixer convergent section 114 inner surface
portion 260 at and downstream of the exit 110 (.theta..sub.3), is
desired in combination with the flow channel diameter of 0.25-20 mm
(more narrowly 0.5-5 mm). FIG. 3A further shows an inner surface
portion 262 of the convergent section 114 spaced upstream of the
exit 110 and forming a brief chamfer having a half angle
.theta..sub.4 and a length L.sub.2. The chamfer serves to reduce
recirculation of suction flow when the flow comes out from suction
inlet and into the mixing chamber plenum. .theta..sub.4 may be
greater than .theta..sub.3. .theta..sub.3 over a region near the
exit and extending downstream therefrom (e.g., by a length of
several times the diameter of the motive nozzle exit) and
.theta..sub.2 over a similar adjacent length of the motive nozzle
upstream of the exit 110) largely influence the radial velocity
component in view of their radial positions and the flow rate. The
angle .theta. may then be chosen, in view of any other geometric
conditions, to further minimize losses upstream of the portion
262.
[0028] The exemplary ejector body is shown as a modular assembly
(e.g., of machined metal/alloy components 202, 204, 206). However,
alternative unitary constructions are possible. The modular
construction may ease optimizing of length for the intended
operating condition. For example, different central body portions
204 may be used with given upstream and downstream
sections/portions 202 and 206. The different central sections 204
may have varying convergent section lengths and/or mixing section
lengths and/or overall lengths to provide desired flow properties
and compactness. The exemplary configuration of a precision
machined central boss (e.g., of circular transverse section) 234
protruding from the upstream face 235 of the downstream section 206
and received in a mating compartment 236 in the downstream face 237
of the section 204 may help ensure precise radial registration of
the portions 204 and 206 so that there is little relative
displacement of the centralized local central axis relative to the
nominal/intended central axis 500. An exemplary high tolerance on
such radial displacement is a maximum of 0.5 mm. Lower tolerances
are 0.1 mm, 0.02 mm, and a highest tolerance of 0.005 mm. Similar
tolerances may be associated with the radial position of the motive
nozzle. In the exemplary configuration, it was impractical to
provide a similar boss-to-compartment engagement between the
sections 202 and 204. Accordingly, the radial positioning is
ensured via two or more pins 240 (e.g., round stainless steel) with
respective first and second end portions received in respective
compartments (bores) 242 of the sections 202 and 204 extending from
a respective downstream face 243 and upstream face 244.
[0029] Via selection of different lengths for the upstream body
portion 202 or via one or more appropriate spacers 248 between the
motive nozzle and the base of the chamber 232, axial position of
the motive nozzle may be set to a desired value. The exemplary
motive nozzle is not rigidly axially secured to the body section
202. Rather, a precision stem portion 250 of the nozzle is
accommodated in the axial bore 220 to provide appropriately precise
radial positioning. Pressure in the chamber 232 drives the nozzle
222 upstream so that a shoulder 252 of nozzle butts against a base
of the chamber (directly or via the one or more spacers) to provide
the desired axial positioning.
[0030] There may be more than one or even more than two secondary
inlets. FIG. 4 shows a ejector 300 having a pair of diametrically
opposite secondary inlet passageways 218 (218A&B) formed by
associated bores and fittings otherwise similar to that of FIG. 3.
For ease of illustration, only separate A and B instances of the
secondary inlets (42A&B), passageways (218A&B), passageway
terminal portions (230A&B), and their associated axes
(502A&B) are separately called out. Other variations involve a
greater number of such passageways evenly angularly spaced about
the axis. Such a configuration may offer one or more advantages
relative to the configuration of FIG. 3. For example, there may be
more uniform circumferential distribution of the secondary/suction
flow around the primary/motive flow. This may lead to improved
mixing and some combination of improved efficiency and/or
permitting reduced axial length.
[0031] In the exemplary overall system configuration, flow from the
heat rejection heat exchanger may be split (e.g., via a
Y-fitting-not shown) to separately feed the two secondary
passageways.
[0032] FIG. 5 shows an ejector 400 wherein the terminal portions of
the passageways 218'A, 218'B are at an angle to associated upstream
portions as the secondary passageways centerlines may curve or have
an abrupt angular change. The exemplary terminal portions are
formed by terminal portions 412 extending to ends 414 of
bent/curving conduits 410A, 410B replacing the secondary fittings
and extending into the chamber 232. Exemplary metal conduits 410A,
410B or portions of an assembly may be inserted from inside the
chamber prior to installation of the motive nozzle and assembly of
the body sections to each other.
[0033] FIG. 6 shows an ejector 600 with relatively lengthened
fittings 226'' which penetrate/protrude into the chamber 232. The
exemplary fitting downstream/outlet ends 227'' are at a right angle
relative to the associated axis 502 and their center defines the
location 518''.
[0034] The ejectors and associated vapor compression systems may be
fabricated from conventional materials and components using
conventional techniques appropriate for the particular intended
uses. Control may also be via conventional methods. Although the
exemplary ejectors are shown omitting a control needle, such a
needle and actuator may, however, be added.
[0035] Although an embodiment is described above in detail, such
description is not intended for limiting the scope of the present
disclosure. It will be understood that various modifications may be
made without departing from the spirit and scope of the disclosure.
For example, when implemented in the remanufacturing of an existing
system or the reengineering of an existing system configuration,
details of the existing configuration may influence or dictate
details of any particular implementation. Accordingly, other
embodiments are within the scope of the following claims.
* * * * *