U.S. patent application number 15/213458 was filed with the patent office on 2018-01-25 for caloric heat pump system.
The applicant listed for this patent is Haier US Appliance Solutions, Inc.. Invention is credited to David G. Beers, Michael Alexander Benedict, Michael Goodman Schroeder.
Application Number | 20180023854 15/213458 |
Document ID | / |
Family ID | 60988363 |
Filed Date | 2018-01-25 |
United States Patent
Application |
20180023854 |
Kind Code |
A1 |
Schroeder; Michael Goodman ;
et al. |
January 25, 2018 |
CALORIC HEAT PUMP SYSTEM
Abstract
A caloric heat pump system includes a plurality of stages, a
plurality of conduits and a plurality of flow restrictors. Each
stage includes a caloric material disposed within a respective
chamber of a plurality of chambers. Each conduit is coupled to a
regenerator housing at a respective one of the plurality of
chambers. Each flow restrictor is coupled to the regenerator
housing or a respective one of the plurality of conduits. A related
method for regulating fluid flow through a plurality of stages of a
caloric heat pump is also provided.
Inventors: |
Schroeder; Michael Goodman;
(Louisville, KY) ; Beers; David G.; (Elizabeth,
IN) ; Benedict; Michael Alexander; (Louisville,
KY) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Haier US Appliance Solutions, Inc. |
Wilmington |
DE |
US |
|
|
Family ID: |
60988363 |
Appl. No.: |
15/213458 |
Filed: |
July 19, 2016 |
Current U.S.
Class: |
62/3.1 |
Current CPC
Class: |
Y02B 30/66 20130101;
F04B 9/042 20130101; F25B 2341/0661 20130101; F25B 41/06 20130101;
F25B 21/00 20130101; F25B 41/04 20130101; F04B 1/053 20130101; Y02B
30/00 20130101; F25B 2321/0021 20130101; F04B 1/0413 20130101 |
International
Class: |
F25B 21/00 20060101
F25B021/00; F04B 9/04 20060101 F04B009/04; F04B 1/053 20060101
F04B001/053; F25B 41/06 20060101 F25B041/06; F25B 41/04 20060101
F25B041/04 |
Claims
1. A caloric heat pump system, comprising: a regenerator housing
comprising a plurality of chambers; a plurality of stages, each
stage comprising a caloric material disposed within a respective
chamber of the plurality of chambers; a plurality of conduits, each
conduit coupled to the regenerator housing at a respective one of
the plurality of chambers; a pump coupled to the conduits of the
plurality of conduits, the pump operable to circulate a working
fluid through the conduits of the plurality of conduits and the
stages of the plurality of stages; and a plurality of flow
restrictors, each flow restrictor coupled to the regenerator
housing or a respective one of the plurality of conduits, the flow
restrictors of the plurality of flow restrictors configured such
that a flow rate of the working fluid through each stage of the
plurality of stages is uniform.
2. The caloric heat pump system of claim 1, wherein the flow
restrictors of the plurality of flow restrictors comprise at least
one of an orifice, a needle valve or a pinch valve.
3. The caloric heat pump system of claim 1, wherein the flow
restrictors of the plurality of flow restrictors are orifices and
are positioned on the regenerator housing.
4. The caloric heat pump system of claim 1, wherein the flow
restrictors of the plurality of flow restrictors are needle valves
or pinch valves and each flow restrictor is coupled to the
respective one of the plurality of conduits.
5. The caloric heat pump system of claim 1, wherein the plurality
of stages comprises four stages and at least two of the four stages
are plumbed in parallel with the conduits of the plurality of
conduits such that working fluid from the pump simultaneously flows
through the at least two of the four stages during operation of the
pump.
6. The caloric heat pump system of claim 5, wherein the pump
comprises a pair of pistons.
7. The caloric heat pump system of claim 6, wherein the pump
further comprises a cam and a motor, the cam coupled to the motor
such that the cam is rotatable with the motor, each piston of the
pair of pistons having a follower positioned on the cam.
8. The caloric heat pump system of claim 1, the flow rate of the
working fluid through each stage of the plurality of stages is
within five percent of one another.
9. The caloric heat pump system of claim 1, wherein the caloric
material is a magneto-caloric material.
10. The caloric heat pump system of claim 1, further comprising: a
first heat exchanger; and a second heat exchanger separate from the
first heat exchanger, wherein the pump is operable to circulate the
heat transfer fluid between the first and second heat exchangers
and the plurality of stages.
11. A caloric heat pump system, comprising: a regenerator housing
comprising a plurality of chambers; a plurality of stages, each
stage comprising a caloric material disposed within a respective
chamber of the plurality of chambers; a plurality of conduits, each
conduit coupled to the regenerator housing at a respective one the
plurality of chambers; a pump coupled to the conduits of the
plurality of conduits, the pump operable to circulate a working
fluid through the conduits of the plurality of conduits and the
stages of the plurality of stages; and a plurality of flow
restrictors, each flow restrictor coupled to the regenerator
housing or a respective one of the plurality of conduits, the flow
restrictors of the plurality of flow restrictors configured such
that a flow rate of the working fluid through each stage of the
plurality of stages is within five percent of one another, wherein
the flow restrictors of the plurality of flow restrictors comprise
at least one of an orifice, a needle valve or a pinch valve.
12. The caloric heat pump system of claim 11, wherein the flow
restrictors of the plurality of flow restrictors are orifices and
are positioned on the regenerator housing.
13. The caloric heat pump system of claim 11, wherein the flow
restrictors of the plurality of flow restrictors are needle valves
or pinch valves and each flow restrictor is coupled to the
respective one of the plurality of conduits.
14. The caloric heat pump system of claim 11, wherein the plurality
of stages comprises four stages and at least two of the four stages
are plumbed in parallel with the conduits of the plurality of
conduits such that working fluid from the pump simultaneously flows
through the at least two of the four stages during operation of the
pump.
15. The caloric heat pump system of claim 14, wherein the pump
comprises a pair of pistons.
16. The caloric heat pump system of claim 15, wherein the pump
further comprises a cam and a motor, the cam coupled to the motor
such that the cam is rotatable with the motor, each piston of the
pair of pistons having a follower positioned on the cam.
17. The caloric heat pump system of claim 11, wherein the caloric
material is a magneto-caloric material.
18. The caloric heat pump system of claim 11, further comprising: a
first heat exchanger; and a second heat exchanger separate from the
first heat exchanger, wherein the pump is operable to circulate the
heat transfer fluid between the first and second heat exchangers
and the plurality of stages.
19. A method for regulating fluid flow through a plurality of
stages of a caloric heat pump, the method comprising flowing a
fluid through each stage of the plurality of stages; measuring a
flow rate of the fluid through each stage of the plurality of
stages; and adjusting a plurality of flow restrictors such that the
flow rate of fluid through each stage of the plurality of stages is
uniform.
20. The method of claim 19, wherein the flow rate of a working
fluid through each stage of the plurality of stages is within five
percent of one another after said step of adjusting.
Description
FIELD OF THE INVENTION
[0001] The subject matter of the present disclosure relates
generally to caloric heat pump systems, such as magneto-caloric
heat pump systems.
BACKGROUND OF THE INVENTION
[0002] Conventional refrigeration technology typically utilizes a
heat pump that relies on compression and expansion of a fluid
refrigerant to receive and reject heat in a cyclic manner so as to
effect a desired temperature change or i.e. transfer heat energy
from one location to another. This cycle can be used to provide
e.g., for the receiving of heat from a refrigeration compartment
and the rejecting of such heat to the environment or a location
that is external to the compartment. Other applications include air
conditioning of residential or commercial structures. A variety of
different fluid refrigerants have been developed that can be used
with the heat pump in such systems.
[0003] While improvements have been made to such heat pump systems
that rely on the compression of fluid refrigerant, at best such can
still only operate at about forty-five percent or less of the
maximum theoretical Carnot cycle efficiency. Also, some fluid
refrigerants have been discontinued due to environmental concerns.
The range of ambient temperatures over which certain
refrigerant-based systems can operate may be impractical for
certain locations. Other challenges with heat pumps that use a
fluid refrigerant exist as well.
[0004] Magneto-caloric materials (MCMs), i.e. materials that
exhibit the magneto-caloric effect, provide a potential alternative
to fluid refrigerants for heat pump applications. In general, the
magnetic moments of an MCM will become more ordered under an
increasing, externally applied magnetic field and cause the MCM to
generate heat. Conversely, decreasing the externally applied
magnetic field will allow the magnetic moments of the MCM to become
more disordered and allow the MCM to absorb heat. Some MCMs exhibit
the opposite behavior, i.e. generating heat when the magnetic field
is removed (which are sometimes referred to as para-magneto-caloric
material but both types are referred to collectively herein as
magneto-caloric material or MCM). The theoretical Carnot cycle
efficiency of a refrigeration cycle based on an MCM can be
significantly higher than for a comparable refrigeration cycle
based on a fluid refrigerant. As such, a heat pump system that can
effectively use an MCM would be useful.
[0005] Challenges exist to the practical and cost competitive use
of an MCM, however. In addition to the development of suitable
MCMs, equipment that can attractively utilize an MCM is still
needed. Currently proposed equipment may require relatively large
and expensive magnets, may be impractical for use in e.g.,
appliance refrigeration, and may not otherwise operate with enough
efficiency to justify capital cost. Additionally, manufacturing
MCMs with uniform flow paths is challenging. Heat pump system
having MCMs with different flow restrictions often provide uneven
fluid flow through the MCMs and reduced efficiency.
[0006] Accordingly, a heat pump system that can address certain
challenges, such as those identified above, would be useful. Such a
heat pump system that can also be used in e.g., a refrigerator
appliance would also be useful.
BRIEF DESCRIPTION OF THE INVENTION
[0007] The present subject matter provides a caloric heat pump
system. The caloric heat pump system includes a plurality of
stages, a plurality of conduits and a plurality of flow
restrictors. Each stage includes a caloric material disposed within
a respective chamber of a plurality of chambers. Each conduit is
coupled to a regenerator housing at a respective one of the
plurality of chambers. Each flow restrictor is coupled to the
regenerator housing or a respective one of the plurality of
conduits. A related method for regulating fluid flow through a
plurality of stages of a caloric heat pump is also provided.
Additional aspects and advantages of the invention will be set
forth in part in the following description, or may be apparent from
the description, or may be learned through practice of the
invention.
[0008] In a first exemplary embodiment, a caloric heat pump system
is provided. The caloric heat pump system includes a regenerator
housing having a plurality of chambers. The caloric heat pump
system also includes a plurality of stages, a plurality of conduits
and a plurality of flow restrictors. Each stage includes a caloric
material disposed within a respective chamber of the plurality of
chambers. Each conduit is coupled to the regenerator housing at a
respective one of the plurality of chambers. A pump is coupled to
the conduits of the plurality of conduits. The pump is operable to
circulate a working fluid through the conduits of the plurality of
conduits and the stages of the plurality of stages. Each flow
restrictor is coupled to the regenerator housing or a respective
one of the plurality of conduits. The flow restrictors of the
plurality of flow restrictors are configured such that a flow rate
of the working fluid through each stage of the plurality of stages
is uniform.
[0009] In a second exemplary embodiment, a caloric heat pump system
is provided. The caloric heat pump system includes a regenerator
housing with a plurality of chambers. The caloric heat pump system
also includes a plurality of stages, a plurality of conduits and a
plurality of flow restrictors. Each stage includes a caloric
material disposed within a respective chamber of the plurality of
chambers. Each conduit is coupled to the regenerator housing at a
respective one of the plurality of chambers. A pump is coupled to
the conduits of the plurality of conduits. The pump is operable to
circulate a working fluid through the conduits of the plurality of
conduits and the stages of the plurality of stages. Each flow
restrictor is coupled to the regenerator housing or a respective
one of the plurality of conduits. The flow restrictors of the
plurality of flow restrictors are configured such that a flow rate
of the working fluid through each stage of the plurality of stages
is within five percent of one another. The flow restrictors of the
plurality of flow restrictors include at least one of an orifice, a
needle valve or a pinch valve.
[0010] In a third exemplary embodiment, a method for regulating
fluid flow through a plurality of stages of a caloric heat pump is
provided. The method includes flowing a fluid through each stage of
the plurality of stages, measuring a flow rate of the fluid through
each stage of the plurality of stages and adjusting a plurality of
flow restrictors such that the flow rate of fluid through each
stage of the plurality of stages is uniform.
[0011] These and other features, aspects and advantages of the
present invention will become better understood with reference to
the following description and appended claims. The accompanying
drawings, which are incorporated in and constitute a part of this
specification, illustrate embodiments of the invention and,
together with the description, serve to explain the principles of
the invention.
BRIEF DESCRIPTION OF THE DRAWINGS
[0012] A full and enabling disclosure of the present invention,
including the best mode thereof, directed to one of ordinary skill
in the art, is set forth in the specification, which makes
reference to the appended figures.
[0013] FIG. 1 is a refrigerator appliance in accordance with an
exemplary embodiment of the present disclosure.
[0014] FIG. 2 is a schematic illustration of certain components of
a heat pump system positioned in the exemplary refrigerator
appliance of FIG. 1.
[0015] FIG. 3 is a schematic illustration of certain components of
the heat pump system of FIG. 2, with a first stage of MCM within a
magnetic field and a second stage of MCM out of a magnetic field,
in accordance with an exemplary embodiment of the present
disclosure.
[0016] FIG. 4 is a schematic illustration of certain components of
the exemplary heat pump system of FIG. 2, with the first stage of
MCM out of the magnetic field and the second stage of MCM within
the magnetic field.
[0017] FIG. 5 is a front view of an exemplary caloric heat pump of
the heat pump system of FIG. 2, with first stages of MCM within
magnetic fields and second stages of MCM out of magnetic
fields.
[0018] FIG. 6 is a front view of the exemplary caloric heat pump of
the heat pump system of FIG. 2, with first stages of MCM out of
magnetic fields and second stages of MCM within magnetic
fields.
[0019] FIG. 7 is a top view of a regenerator housing and MCM stages
of the exemplary caloric heat pump of FIG. 5.
[0020] FIG. 8 is a top view of certain components of the exemplary
caloric heat pump of FIG. 5.
[0021] FIG. 9 is a chart illustrating movement of a regenerator
housing and associated MCM stages in accordance with an exemplary
embodiment of the present disclosure.
[0022] FIG. 10 is a chart illustrating operation of pumps to
actively flow working fluid in accordance with an exemplary
embodiment of the present disclosure.
[0023] FIG. 11 is a schematic diagram illustrating various
positions and movements there-between of MCM stages in accordance
with an exemplary embodiment of the present disclosure.
[0024] FIGS. 12, 13 and 14 provide section views of regenerators
according to various exemplary embodiment of the present subject
matter.
[0025] FIG. 15 provides an elevation view of a pump according to an
exemplary embodiment of the present subject matter.
[0026] FIG. 16 provides a schematic view of an alternative
exemplary arrangement of stages of a heat pump system coupled to
pistons of a pump.
DETAILED DESCRIPTION
[0027] Reference now will be made in detail to embodiments of the
invention, one or more examples of which are illustrated in the
drawings. Each example is provided by way of explanation of the
invention, not limitation of the invention. In fact, it will be
apparent to those skilled in the art that various modifications and
variations can be made in the present invention without departing
from the scope or spirit of the invention. For instance, features
illustrated or described as part of one embodiment can be used with
another embodiment to yield a still further embodiment. Thus, it is
intended that the present invention covers such modifications and
variations as come within the scope of the appended claims and
their equivalents.
[0028] The present subject matter is directed to a caloric heat
pump system for heating or cooling an appliance, such as a
refrigerator appliance. While described in greater detail below in
the context of a magneto-caloric heat pump system, one of skill in
the art will recognize that other suitable caloric materials may be
used in a similar manner to heat or cool an appliance, i.e., apply
a field, move heat, remove the field, move heat. For example,
electro-caloric material heats up and cools down within increasing
and decreasing electric fields. As another example, elasto-caloric
material heats up and cools down when exposed to increasing and
decreasing mechanical strain. As yet another example, baro-caloric
material heats up and cools down when exposed to increasing and
decreasing pressure. Such materials another other similar caloric
materials may be used in place of or in addition to the
magneto-caloric material described below to heat or cool water
within an appliance. Thus, caloric material is used broadly herein
to encompass materials that undergo heating or cooling when exposed
to a changing field from a field generator, where the field
generator may be a magnet, an electric field generator, an actuator
for applying mechanical stress or pressure, etc.
[0029] Referring now to FIG. 1, an exemplary embodiment of a
refrigerator appliance 10 is depicted as an upright refrigerator
having a cabinet or casing 12 that defines a number of internal
storage compartments or chilled chambers. In particular,
refrigerator appliance 10 includes upper fresh-food compartments 14
having doors 16 and lower freezer compartment 18 having upper
drawer 20 and lower drawer 22. Drawers 20, 22 are "pull-out" type
drawers in that they can be manually moved into and out of freezer
compartment 18 on suitable slide mechanisms. Refrigerator 10 is
provided by way of example only. Other configurations for a
refrigerator appliance may be used as well including appliances
with only freezer compartments, only chilled compartments, or other
combinations thereof different from that shown in FIG. 1. In
addition, the heat pump and heat pump system of the present
disclosure is not limited to refrigerator appliances and may be
used in other applications as well such as e.g., air-conditioning,
electronics cooling devices, and others. Thus, it should be
understood that while the use of a heat pump and heat pump system
to provide cooling within a refrigerator is provided by way of
example herein, the present disclosure may also be used to provide
for heating applications as well.
[0030] FIG. 2 is a schematic view of various components of
refrigerator appliance 10, including a refrigeration compartment 30
and a machinery compartment 40. In particular, machinery
compartment 30 includes a heat pump system 52 having a first or
cold side heat exchanger 32 positioned in refrigeration compartment
30 for the removal of heat therefrom. A heat transfer fluid such as
e.g., an aqueous solution, flowing within first heat exchanger 32
receives heat from refrigeration compartment 30 thereby cooling
contents of refrigeration compartment 30. A fan 38 may be used to
provide for a flow of air across first heat exchanger 32 to improve
the rate of heat transfer from refrigeration compartment 30.
[0031] The heat transfer fluid flows out of first heat exchanger 32
by line 44 to heat pump 100. As will be further described herein,
the heat transfer fluid receives additional heat from
magneto-caloric material (MCM) in heat pump 100 and carries this
heat by line 48 to pump 42 and then to second or hot side heat
exchanger 34. Heat is released to the environment, machinery
compartment 40, and/or other location external to refrigeration
compartment 30 using second heat exchanger 34. A fan 36 may be used
to create a flow of air across second heat exchanger 34 and thereby
improve the rate of heat transfer to the environment. Pump 42
connected into line 48 causes the heat transfer fluid to
recirculate in heat pump system 52. Motor 28 is in mechanical
communication with heat pump 100, as will be further described.
[0032] From second heat exchanger 34, the heat transfer fluid
returns by line 50 to heat pump 100 where, as will be further
described below, the heat transfer fluid loses heat to the MCM in
heat pump 100. The now colder heat transfer fluid flows by line 46
to first heat exchanger 32 to receive heat from refrigeration
compartment 30 and repeat the cycle as just described.
[0033] Heat pump system 52 is provided by way of example only.
Other configurations of heat pump system 52 may be used as well.
For example, lines 44, 46, 48, and 50 provide fluid communication
between the various components of heat pump system 52 but other
heat transfer fluid recirculation loops with different lines and
connections may also be employed. For example, pump 42 can also be
positioned at other locations or on other lines in system 52. Still
other configurations of heat pump system 52 may be used as
well.
[0034] FIGS. 3 through 11 illustrate an exemplary heat pump 100 and
components thereof, and the use of such heat pumps 100 with heat
pump system 52, in accordance with exemplary embodiments of the
present disclosure. Components of heat pump 100 may be oriented
relative to a coordinate system for heat pump 100, which may
include a vertical direction V, a transverse direction T, and a
longitudinal direction L all of which may be mutually perpendicular
and orthogonal to one another.
[0035] As shown in FIGS. 5 and 6, heat pump 100 includes one or
more magnet assemblies 110, each of which creates a magnetic field
M. For example, a magnetic field M may be generated by a single
magnet, or by multiple magnets. In exemplary embodiments as
illustrated, a first magnet 112 and a second magnet 114 may be
provided, and the magnetic field M may be generated between magnets
112, 114. Magnets 112, 114 may, for example, have opposite magnetic
polarities such that they either attract or repel each other.
Magnets 112, 114 of magnet assembly 110 may also be spaced apart
from each other, such as along the vertical direction V. A gap 116
may thus be defined between first magnet 112 and second magnet 114,
such as along the vertical direction V.
[0036] Heat pump 100 may further include a support frame 120 which
supports magnet assembl(ies) 110. Magnet assembly 110 may be
connected to support frame 120. For example, each magnet 112, 114
of magnet assembly 110 may be connected to support frame 120. Such
connection in exemplary embodiments is a fixed connection via a
suitable adhesive, mechanical fasteners, and/or a suitable
connecting technique such as welding, brazing, etc. Support
assembly 120 may, for example, support magnets 112, 114 in position
such that gap 114 is defined between magnets 112, 114.
[0037] As illustrated, support frame 120 is an open-style frame,
such that interior portions of support frame 120 are accessible
from exterior to support frame 120 (e.g. in the longitudinal and
transverse directions L, T) and components of heat pump 100 can be
traversed from interior to support frame 120 to exterior to support
frame 120 and vice-versa. For example, support frame 120 may define
one or more interior spaces 122. Multiple interior spaces 122, as
shown, may be partitioned from each other by frame members or other
components of the support frame 120. An interior space 122 may be
contiguous with associated magnets 112, 114 (i.e. magnet assembly
110) and gap 116, such as along the longitudinal direction L.
Support frame 120 may additionally define one or more exterior
spaces 124, each of which includes the exterior environment
proximate support frame 120. Specifically, an exterior space 124
may be contiguous with associated magnets 112, 114 (i.e. magnet
assembly 110) and gap 116, such as along the longitudinal direction
L. An associated interior space 122 and exterior space 124 may be
disposed on opposing sides of associated magnets 112, 114 (i.e.
magnet assembly 110) and gap 116, such as along the longitudinal
direction L. Thus, magnet assembly 110 and gap 116 may be
positioned between an associated interior space 122 and exterior
space 124, e.g., along the lateral direction L.
[0038] As illustrated in FIGS. 5 and 6, support frame 120 and frame
members and other components thereof may include and form one or
more C-shaped portions. A C-shaped portion may, for example, define
an interior space 122 and associated gap 116, and may further
define an associated exterior space 124 as shown.
[0039] In exemplary embodiments as illustrated, a support frame 120
may support two magnet assemblies 110, and may define an interior
space 122, gap 116, and exterior space 124 associated with each of
two magnet assemblies 110. Alternatively, however, a support frame
120 may support only a single magnet assembly 110 or three or more
magnet assemblies 110.
[0040] Various frame members may be utilized to form support frame
120. For example, in some exemplary embodiments, an upper frame
member 126 and a lower frame member 127 may be provided. Lower
frame member 127 may be spaced apart from upper frame member 126
along the vertical axis V. First magnet(s) 112 may be connected to
upper frame member 126, and second magnet(s) 114 may be connected
to lower frame member 127. In exemplary embodiments, upper frame
member 126 and lower frame member 127 may be formed from materials
which have relatively high magnetic permeability, such as iron.
[0041] In some exemplary embodiments, as illustrated in FIGS. 5 and
6, a support frame 120 may further include an intermediate frame
member 128. Intermediate frame member 128 may be disposed and
extend between and connect upper frame member 126 and lower frame
member 127, and may in some exemplary embodiments be integrally
formed with upper and lower frame members 126, 127. As shown,
multiple interior spaces 122 may be partitioned from each other by
intermediate frame member 128. In some exemplary embodiments,
intermediate frame member 128 may be formed from materials which
have relatively high magnetic permeability, such as iron. In other
exemplary embodiments, intermediate frame member 128 may be formed
from materials which have relatively lower magnetic permeability
than those of upper and lower frame members 126, 127. Accordingly,
such materials, termed magnetically shielding materials herein, may
facilitate direction of magnetic flux paths only through upper and
lower frame members 126, 127 and magnet assemblies 110,
advantageously reducing losses in magnetic strength, etc.
[0042] Referring again to FIGS. 3 through 11, heat pump 100 may
further include a plurality of stages, each of which includes a
magneto-caloric material (MCM). In exemplary embodiments, such MCM
stages may be provided in pairs, each of which may for example
include a first stage 130 and a second stage 132. Each stage 130,
132 may include one or more different types of MCM. Further, the
MCM(s) provided in each stage 130, 132 may be the same or may be
different.
[0043] As provided in heat pump 100, each stage 130, 132 may
extend, such as along the transverse direction T, between a first
end portion 134 and a second end portion 136. As discussed herein,
working fluid (also referred to herein as heat transfer fluid or
fluid refrigerant) may flow into each stage 130, 132 and from each
stage 130, 132 through first end portion 134 and second end portion
136. Accordingly, working fluid flowing through a stage 130, 132
during operation of heat pump 100 flows generally along the
transverse direction T between first and second end portions 134,
136 of stages 130, 132.
[0044] Stages 130, 132, such as each pair of stages 130, 132, may
be disposed within regenerator housings 140. Regenerator housing
140 along with stages 130, 132 and optional insulative materials
138 may collectively be referred to as a regenerator assembly. As
shown in FIGS. 5 and 6, a housing 140 includes a body 142 which
defines a plurality of chambers 144, each of which extends along
the transverse direction T between opposing ends of chamber 144.
Chambers 144 of a regenerator housing 140 may thus be arranged in a
linear array along the longitudinal direction L, as shown. Each
stage 130, 132, such as of a pair of stages 130, 132, may be
disposed within one of chambers 144 of a regenerator housing 140.
Accordingly, these stages 130, 132 may be disposed in a linear
array along the longitudinal direction L.
[0045] As illustrated, in exemplary embodiments, each regenerator
housing 140 may include a pair of stages 130, 132. Alternatively,
three, four or more stages 130, 132 may be provided in a
regenerator housing 140.
[0046] The regenerator housing(s) 140 (and associated stages 130,
132) and magnet assembly(s) 110 may be movable relative to each
other, such as along the longitudinal direction L. In exemplary
embodiments as shown, for example, each regenerator housing 140
(and associated stages 130, 132) is movable relative to an
associated magnet assembly 110, such as along the longitudinal
direction L. Alternatively, however, each magnet assembly 110 may
be movable relative to the associated regenerator housing 140 (and
associated stages 130, 132), such as along the longitudinal
direction L.
[0047] Such relative movement between regenerator housing 140 and
an associated magnet assembly 110 causes movement of each stage
130, 132 into the magnetic field M and out of the magnetic field M.
As discussed herein, movement of a stage 130, 132 into the magnetic
field M may cause the magnetic moments of the material to orient
and the MCM to heat (or alternatively cool) as part of the
magneto-caloric effect. When a stage 130, 132 is out of the
magnetic field M, the MCM may thus cool (or alternatively heat) due
to disorder of the magnetic moments of the material.
[0048] For example, a regenerator housing 140 (or an associated
magnet assembly 110) may be movable along the longitudinal
direction L between a first position and a second position. In the
first position (as illustrated for example in FIGS. 3 and 5),
regenerator housing 140 may be positioned such that first stage 130
disposed within the regenerator housing 140 is within the magnetic
field M and second stage 132 disposed within the regenerator
housing 140 is out of the magnetic field M. Notably, being out of
the magnetic field M means that second stage 132 is generally or
substantially uninfluenced by the magnets and resulting magnetic
field M. Accordingly, the MCM of the stage as a whole may not be
actively heating (or cooling) as it would if within the magnetic
field M (and instead may be actively or passively cooling (or
heating) due to such removal of the magnetic field M). In the
second position (as illustrated for example in FIGS. 4 and 6),
regenerator housing 140 may be positioned such that first stage 130
disposed within regenerator housing 140 is out of the magnetic
field M and second stage 132 disposed within regenerator housing
140 is within the magnetic field M.
[0049] Regenerator housing 140 (or an associated magnet assembly
110) is movable along the longitudinal direction L between the
first position and the second position. Such movement along the
longitudinal direction from the first position to the second
position may be referred to herein as a first transition, while
movement along the longitudinal direction from the second position
to the first position may be referred to herein as a second
transition.
[0050] Referring to FIGS. 8 and 9, movement of a regenerator
housing 140 (or an associated magnet assembly 110) may be caused by
operation of motor 26. Motor 26 may be in mechanical communication
with regenerator housing 140 (or magnet assembly 110) and
configured for moving regenerator housing 140 (or magnet assembly
110) along the longitudinal direction L (i.e. between the first
position and second position). For example, a shaft 150 of motor 28
may be connected to a cam. The cam may be connected to the
regenerator housing 140 (or associated magnet assembly 110), such
that relative movement of the regenerator housing 140 and
associated magnet assembly 110 is caused by and due to rotation of
the cam. The cam may, as shown, be rotational about the
longitudinal direction L.
[0051] For example, in some exemplary embodiments as illustrated in
FIGS. 8 and 9, the cam may be a cam cylinder 152. Cam cylinder 152
may be rotational about the longitudinal direction L. A cam groove
154 may be defined in cam cylinder 152, and a follower tab 148 of
regenerator housing 120 may extend into cam groove 154. Rotation of
motor 28 may cause rotation of cam cylinder 152. Cam groove 154 may
be defined in a particularly desired cam profile such that, when
cam cylinder 152 rotates, tab 148 moves along the longitudinal
direction L between the first position and second position due to
the pattern of cam groove 154 and in the cam profile, in turn
causing such movement of regenerator housing 120.
[0052] FIG. 9 illustrates one embodiment of a cam profile which
includes a first position, first transition, second position, and
second transition. Notably, in exemplary embodiments the period
during which a regenerator housing 140 (or an associated magnet
assembly 110) is dwelling in the first position and/or second
position may be longer than the period during which the regenerator
housing 140 (or an associated magnet assembly 110) is moving in the
first transition and/or second transition. Accordingly, the cam
profile defined by the cam defines the first position, the second
position, the first transition, and the second transition. In
exemplary embodiments, the cam profile causes the one of the
regenerator housing or the magnet assembly to dwell in the first
position and the second position for periods of time longer than
time periods in the first transition and second transition.
[0053] Referring again to FIG. 2, in some exemplary embodiments,
lines 44, 46, 48, 50 may facilitate the flow of working fluid
between heat exchangers 32, 34 and heat pump 100. Referring now to
FIGS. 3, 4 and 7, in exemplary embodiments, lines 44, 46, 48, 50
may facilitate the flow of working fluid between heat exchangers
32, 34 and stages 130, 132 of heat pump 100. Working fluid may flow
to and from each stage 130, 132 through various apertures defined
in each stage. The apertures generally define the locations of
working fluid flow to or from each stage. In some exemplary
embodiments as illustrated in FIGS. 3, 4 and 7, multiple apertures
(e.g., two apertures) may be defined in first end 134 and second
end 136 of each stage 130, 132. For example, each stage 130, 132
may define a cold side inlet 162, a cold side outlet 164, a hot
side inlet 166 and a hot side outlet 168. Cold side inlet 162 and
cold side outlet 164 may be defined in each stage 130, 132 at first
end 134 of stage 130, 132, and hot side inlet 166 and hot side
outlet 168 may be defined in each stage 130, 132 at second end 136
of stage 130, 132. The inlets and outlets may provide fluid
communication for the working fluid to flow into and out of each
stage 130, 132, and from or to heat exchangers 32, 34. For example,
a line 44 may extend between cold side heat exchanger 32 and cold
side inlet 162, such that working fluid from heat exchanger 32
flows through line 44 to cold side inlet 162. A line 46 may extend
between cold side outlet 164 and cold side heat exchanger 32, such
that working fluid from cold side outlet 164 flows through line 46
to heat exchanger 32. A line 50 may extend between hot side heat
exchanger 34 and hot side inlet 166, such that working fluid from
heat exchanger 34 flows through line 50 to hot side inlet 166. A
line 48 may extend between hot side outlet 168 and hot side heat
exchanger 34, such that working fluid from hot side outlet 168
flows through line 48 to heat exchanger 34.
[0054] When a regenerator housing 140 (and associated stages 130,
132) is in a first position, a first stage 130 may be within the
magnetic field and a second stage 132 may be out of the magnetic
field. Accordingly, working fluid in first stage 130 may be heated
(or cooled) due to the magneto-caloric effect, while working fluid
in second stage 132 may be cooled (or heated) due to the lack of
magneto-caloric effect. Additionally, when a stage 130, 132 is in
the first position or second position, working fluid may be
actively flowed to heat exchangers 32, 34, such as through inlets
and outlets of the various stages 130, 132. Working fluid may be
generally constant within stages 130, 132 during the first and
second transitions.
[0055] One or more pumps 170, 172 (each of which may be a pump 42
as discussed herein) may be operable to facilitate such active flow
of working fluid when the stages are in the first position or
second position. In exemplary embodiments, each pump is or includes
a reciprocating piston. For example, a single pump assembly may
include two reciprocating pistons. For example, a first pump 170
(which may be or include a piston) may operate to flow working
fluid when the stages 130, 132 are in the first position (such that
stage 130 is within the magnetic field M and stage 132 is out of
the magnetic field M), while a second pump 172 (which may be or
include a piston) may operate to flow working fluid when the stages
130, 132 are in the second position (such that stage 132 is within
the magnetic field M and stage 130 is out of the magnetic field M).
Operation of a pump 170, 172 may cause active flow of working fluid
through the stages 130, 132, heat exchangers 32, 34, and system 52
generally. Each pump 170, 172 may be in fluid communication with
the stages 130, 132 and heat exchangers 32, 34, such as on various
lines between stages 130, 132 and heat exchangers 32, 34. In
exemplary embodiments as shown, the pumps 170, 172 may be on "hot
side" lines between the stages 130, 132 and heat exchanger 34 (i.e.
on lines 48). Alternatively, the pumps 170, 172 may be on "cold
side" lines between the stages 130, 132 and heat exchanger 32 (i.e.
on lines 44). Referring briefly to FIG. 10, operation of the pumps
170, 172 relative to movement of a regenerator housing 140 and
associated stages 130, 132 through a cam profile is illustrated.
First pump 170 may operate when the stages are in the first
position, and second pump 172 may operate when the stages are in
the second position.
[0056] Working fluid may be flowable from a stage 130, 132 through
hot side outlet 168 and to stage 130, 132 through cold side inlet
162 when the stage is within the magnetic field M. Working fluid
may be flowable from a stage 130, 132 through cold side outlet 164
and to the stage through hot side inlet 166 during movement of
stage 130, 132 when the stage is out of the magnetic field M.
Accordingly, and referring now to FIGS. 3 and 4, a first flow path
180 and a second flow path 182 may be defined. Each flow path 180
may include flow through a first stage 130 and second stage 132, as
well as flow through cold side heat exchanger 32 and hot side heat
exchanger 34. The flow of working fluid may occur either along the
first flow path 180 or the second flow path 182, depending on the
positioning of the first and second stages 130, 132.
[0057] FIG. 3 illustrates a first flow path 180, which may be
utilized in the first position. In the first position, first stage
130 is within the magnetic field M, and second stage 132 is out of
the magnetic field M. Activation and operation of pump 170 may
facilitate active working fluid flow through first flow path 180.
As shown, working fluid may flow from cold side heat exchanger 32
through line 44 and cold side inlet 162 of first stage 130 to the
first stage 130, from first stage 130 through hot side outlet 168
and line 48 of first stage 130 to hot side heat exchanger 34, from
hot side heat exchanger 34 through line 50 and hot side inlet 166
of second stage 132 to second stage 132, and from second stage 132
through cold side outlet 164 and line 46 of second stage 132 to
cold side heat exchanger 32.
[0058] FIG. 4 illustrates a second flow path 182, which may be
utilized during the second position. In the second position, second
stage 132 is within the magnetic field M, and first stage 130 is
out of the magnetic field M. Activation and operation of pump 172
may facilitate active working fluid flow through second flow path
182. As shown, working fluid may flow from cold side heat exchanger
32 through line 44 and cold side inlet 162 of second stage 132 to
second stage 132, from second stage 132 through hot side outlet 168
and line 48 of second stage 132 to hot side heat exchanger 34, from
hot side heat exchanger 34 through line 50 and hot side inlet 166
of first stage 130 to first stage 130, and from first stage 130
through cold side outlet 164 and line 46 of first stage 130 to cold
side heat exchanger 32.
[0059] Notably, check valves 190 may in some exemplary embodiments
be provided on the various lines 44, 46, 48, 50 to prevent backflow
there-through. Check valves 190, in combination with differential
pressures during operation of heat pump 100, may thus generally
prevent flow through the improper flow path when working fluid is
being actively flowed through one of flow paths 190, 192.
[0060] For example, flexible lines 44, 46, 48, 50 may each be
formed from one of a polyurethane, a rubber, or a polyvinyl
chloride, or another suitable polymer or other material. In
exemplary embodiments, lines 44, 46, 48, 50 may further be fiber
impregnated, and thus include embedded fibers, or may be otherwise
reinforced. For example, glass, carbon, polymer or other fibers may
be utilized, or other polymers such as polyester may be utilized to
reinforce lines 44, 46, 48, 50.
[0061] FIG. 11 illustrates an exemplary method of the present
disclosure using a schematic representation of associated stages
130, 132 of MCM during dwelling in and movement between the various
positions as discussed herein. With regard to first stage 130,
during step 200, which corresponds to the first position, stage 130
is fully within magnetic field M, which causes the magnetic moments
of the material to orient and the MCM to heat as part of the
magneto caloric effect. Further, pump 170 is activated to actively
flow working fluid in first flow path 180. As indicated by arrow
Q.sub.H-OUT, working fluid in stage 130, now heated by the MCM, can
travel out of stage 130 and along line 48 to second heat exchanger
34. At the same time, and as indicated by arrow Q.sub.H-IN, working
fluid from first heat exchanger 32 flows into stage 130 from line
44. Because working fluid from first heat exchanger 32 is
relatively cooler than the MCM in stage 130, the MCM will lose heat
to the working fluid.
[0062] In step 202, stage 130 is moved from the first position to
the second position in the first transition. During the time in the
first transition, working fluid dwells in the MCM of stage 130.
More specifically, the working fluid does not actively flow through
stage 130.
[0063] In step 204, stage 130 is in the second position and thus
out of magnetic field M. The absence or lessening of the magnetic
field is such that the magnetic moments of the material become
disordered and the MCM absorbs heat as part of the magnetocaloric
effect. Further, pump 172 is activated to actively flow working
fluid in the second flow path 182. As indicated by arrow
Q.sub.C-OUT, working fluid in stage 130, now cooled by the MCM, can
travel out of stage 130 and along line 46 to first heat exchanger
32. At the same time, and as indicated by arrow Q.sub.C-IN, working
fluid from second heat exchanger 34 flows into stage 112 from line
50 when stage 130 is in the second transition. Because working
fluid from second heat exchanger 34 is relatively warmer than the
MCM in stage 130, the MCM will lose some of its heat to the working
fluid. The working fluid now travels along line 46 to first heat
exchanger 32 to receive heat and cool refrigeration compartment
30.
[0064] In step 206, stage 130 is moved from the second position to
the first position in the second transition. During the time in the
second transition, the working fluid dwells in the MCM of stage
130. More specifically, the working fluid does not actively flow
through stage 130.
[0065] With regard to second stage 132, during step 200, which
corresponds to the first position, second stage 132 is out of
magnetic field M. The absence or lessening of the magnetic field is
such that the magnetic moments of the material become disordered
and the MCM absorbs heat as part of the magneto-caloric effect.
Further, pump 170 is activated to actively flow working fluid in
first flow path 180. As indicated by arrow Q.sub.C-OUT, working
fluid in stage 132, now cooled by the MCM, can travel out of stage
132 and along line 46 to first heat exchanger 32. At the same time,
and as indicated by arrow Q.sub.C-IN, working fluid from second
heat exchanger 34 flows into stage 112 from line 50 when stage 132
is in the second transition. Because working fluid from second heat
exchanger 34 is relatively warmer than the MCM in stage 132, the
MCM will lose some of its heat to the working fluid. The working
fluid now travels along line 46 to first heat exchanger 32 to
receive heat and cool the refrigeration compartment 30.
[0066] In step 202, stage 132 is moved from the first position to
the second position in the first transition. During the time in the
first transition, the working fluid dwells in the MCM of stage 132.
More specifically, the working fluid does not actively flow through
stage 132.
[0067] In step 204, stage 132 is in the second position and thus
fully within magnetic field M, which causes the magnetic moments of
the material to orient and the MCM to heat as part of the magneto
caloric effect. Further, pump 172 is activated to actively flow
working fluid in the second flow path 182. As indicated by arrow
Q.sub.H-OUT, working fluid in stage 132, now heated by the MCM, can
travel out of stage 132 and along line 48 to second heat exchanger
34. At the same time, and as indicated by arrow Q.sub.H-IN, working
fluid from first heat exchanger 32 flows into stage 132 from line
44. Because working fluid from first heat exchanger 32 is
relatively cooler than the MCM in stage 132, the MCM will lose heat
to the working fluid.
[0068] In step 206, stage 132 is moved from the second position to
the first position in the second transition. During the time in the
second transition, working fluid dwells in the MCM of stage 132.
More specifically, the working fluid does not actively flow through
stage 132.
[0069] FIGS. 12, 13 and 14 provide section views of regenerators
according to various exemplary embodiment of the present subject
matter. As discussed in greater detail below the regenerators shown
in FIGS. 12, 13 and 14 include features for assisting with
providing even flow of working fluid into the regenerators. Even
working fluid flow into the regenerators can limit or reduce dead
fluid volume within the regenerators and/or provide more even fluid
flow from the regenerators. The regenerators shown in FIGS. 12, 13
and 14 may be used in any suitable caloric heat pump, such as heat
pump 100 described above.
[0070] Turning now to FIG. 12, a regenerator 200 according to an
exemplary embodiment of the present subject matter is provided.
Regenerator 200 includes a regenerator housing 210 and a stage 220.
Regenerator housing 210 defines a longitudinal direction LL and a
transverse direction TT that are perpendicular to each other.
Regenerator housing 210 may hollow and define a chamber 212
therein. Regenerator housing 210 (e.g., and chamber 212) extends,
e.g., along the longitudinal direction LL, between a first end
portion 214 and a second end portion 216. Thus, regenerator housing
210 may be hollow between first and second end portions 214, 216 of
regenerator housing 210, e.g., along the longitudinal direction
LL.
[0071] Stage 220 includes a caloric material, such as a
magneto-caloric material, and is disposed within chamber 212 of
regenerator housing 210. In particular, stage 220 may be disposed
within chamber 212 of regenerator housing 210 between the first and
second end portions 214, 216 of regenerator housing 210. Working
fluid may flow through the stage 220 between first and second end
portions 214, 216 of regenerator housing 210 within regenerator
housing 210.
[0072] Regenerator 200 also includes a pair of caps that assist
with sealing chamber 212 of regenerator housing 210 in order to
define a flow path for working fluid through regenerator 200. In
particular, regenerator 200 includes a first cap 230 and a second
cap 240. First cap 230 and second cap 240 are mounted to
regenerator housing 210, e.g., such that first cap 230 and second
cap 240 are positioned at opposite ends of regenerator housing 210
along the longitudinal direction LL and/or spaced apart from each
other along the longitudinal direction LL. As an example, first cap
230 is mounted or affixed to regenerator housing 210 at first end
portion 214 of regenerator housing 210, and second cap 240 is
mounted or affixed to regenerator housing 210 at second end portion
216 of regenerator housing 210.
[0073] First cap 230 and second cap 240 may be constructed of any
suitable material. For example, first cap 230 and second cap 240
may be constructed of plastic, such as molded or additively formed
plastic. Regenerator housing 210 may also be formed of plastic, and
first cap 230 and second cap 240 may be mounted to regenerator
housing 210 using any suitable method or mechanism, such as screw
threads, spin welding, ultrasonic welding, adhesive, etc. In
certain exemplary embodiments, first and second caps 230, 240 may
be uniformly shaped. In alternative exemplary embodiments, first
and second caps 230, 240 may have different shapes.
[0074] Stage 220 is disposed within chamber 212 between first cap
230 and second cap 240. In particular, first cap 230 and second cap
240 may contact stage 220 within chamber 212 such that stage 220 is
held or supported within chamber 212 between first cap 230 and
second cap 240. As shown in FIG. 12, first cap 230 and stage 220
may extend across chamber 212 at first end portion 214 of
regenerator housing 210. Similarly, second cap 240 and stage 220
may extend across chamber 212 at second end portion 216 of
regenerator housing 210. Thus, first cap 230, second cap 240 and
stage 220 may have common widths, e.g., along the transverse
direction TT. In particular, first cap 230, second cap 240 and
stage 220 may extend across chamber 212, e.g., along the transverse
direction TT, in order to prevent leakage or bypass of working
fluid within chamber 212 around first cap 230, second cap 240
and/or stage 220.
[0075] First cap 230 defines an inlet 232 and an outlet 234 that
allow flow of working fluid through first cap 230. Similarly,
second cap 240 defines an inlet 242 and an outlet 244 that allow
flow of working fluid through second cap 240. Outlet 232 of first
cap 230 and outlet 242 of second cap 240 may be positioned at
and/or contiguous with chamber 212. Thus, working fluid may flow
into or out of chamber 212 via outlet 232 of first cap 230 and/or
outlet 242 of second cap 240, depending upon the direction of fluid
flow through chamber 212.
[0076] Inlet 232 of first cap 230 and outlet 234 of first cap 230
each define an area in a respective plane that is perpendicular to
the longitudinal direction LL. Thus, the area of inlet 232 of first
cap 230 and the area of outlet 234 of first cap 230 may be
perpendicular to direction of the flow of working fluid through
first cap 230 at inlet 232 of first cap 230 and outlet 234 of first
cap 230. In addition, inlet 242 of second cap 240 and outlet 244 of
second cap 240 each define an area in a respective plane that is
perpendicular to the longitudinal direction LL. Thus, the area of
inlet 242 of second cap 240 and the area of outlet 244 of second
cap 240 may be perpendicular to direction of the flow of working
fluid through second cap 240 at inlet 242 of second cap 240 and
outlet 244 of second cap 240.
[0077] The area of inlet 232 of first cap 230 may be less than the
area of outlet 234 of first cap 230. Similarly, the area of inlet
242 of second cap 240 may be less than the area of outlet 244 of
second cap 240. Such sizing of the inlets 232, 242 of first and
second caps 230, 240 relative to the outlets 234, 244 of first and
second caps 230, 240 may assist with regulating flow of working
fluid through chamber 212 of regenerator housing 210 and/or stage
220. For example, such sizing may facilitate even flow of working
fluid into chamber 212 and stage 220, and even working fluid flow
into chamber 212 and stage 220 can limit or reduce dead fluid
volume within chamber 212 or stage 220 and/or provide more even
fluid flow from chamber 212 or stage 220. In particular, the area
of inlet 232 of first cap 230 may be less than the area of outlet
234 of first cap 230 such that a velocity of working fluid at inlet
232 of first cap 230 is greater than a velocity of working fluid at
outlet 234 of first cap 230. Second cap 240 may have similar
working fluid velocities therein.
[0078] The area of inlet 232 of first cap 230 may be less than the
area of outlet 234 of first cap 230 by certain ratios in exemplary
embodiments. As an example, the area of outlet 234 of first cap 230
may be at least four times greater than the area of inlet 232 of
first cap 230. As another example, the area of outlet 234 of first
cap 230 may be at least ten times greater than the area of inlet
232 of first cap 230. Such sizing of the area of outlet 234 of
first cap 230 relative to the area of inlet 232 of first cap 230
may assist with significantly reducing the velocity of working
fluid at outlet 234 of first cap 230 relative to the velocity of
working fluid at inlet 232 of first cap 230 and thereby limit or
reduce dead fluid volume within chamber 212 or stage 220 and/or
provide more even fluid flow from chamber 212 or stage 220.
Features of second cap may be similarly proportioned.
[0079] First cap 230 may have various shapes such that area of
inlet 232 of first cap 230 is less than the area of outlet 234 of
first cap 230, and second cap 240 may have various shapes such that
area of inlet 242 of second cap 240 is less than the area of outlet
244 of second cap 240. For example, with reference to FIG. 12,
outlet 234 of first cap 230 may be tapered, e.g., such that the
area of outlet 234 decreases along the longitudinal direction LL
from chamber 212 towards inlet 232 of first cap 230. Thus, outlet
234 of first cap 230 may be conical or otherwise funneled in
certain exemplary embodiments. Still referring to FIG. 12, inlet
232 of first cap 230 may include a plurality of channels 236 that
collectively define the area of inlet 232 of first cap 230.
Channels 236 of inlet 232 of first cap 230 may extend towards or
outlet 234 of first cap 230, e.g., along the longitudinal direction
LL. In addition, channels 236 may be spaced apart from each other
along the transverse direction TT. First cap 230 may include any
suitable number of channels 236. For example, as shown in FIG. 12,
first cap 230 may include two channels 236. In alternative
exemplary embodiments, first cap 230 may define three, four, five
or more channels 236 or first cap 230 may define only one
channel.
[0080] As shown in FIGS. 13 and 14, caps may have different shapes
in alternative exemplary embodiments. A regenerator 300 according
to another exemplary embodiment of the present subject matter is
provided in FIG. 13, and a regenerator 400 according to an
additional exemplary embodiment of the present subject matter is
provided in FIG. 14. Regenerator 300 and regenerator 400 include
similar components and are constructed in a similar manner to
regenerator 200 (FIG. 12). For example, regenerator 300 includes a
regenerator housing 310, a stage 320, a first cap 330 and a second
cap 340. Similarly, regenerator 400 includes a regenerator housing
410, a stage 420, a first cap 430 and a second cap 440.
[0081] Turning now to FIG. 13, first cap 330 of regenerator 300 has
an inlet 332 and an outlet 334, and second cap 340 has an inlet 342
and an outlet 344. The area of inlet 332 of first cap 330 may be
less than the area of outlet 334 of first cap 330, and the area of
inlet 342 of second cap 340 may be less than the area of outlet 344
of second cap 340. The area of outlet 334 of first cap 330 may be
constant, e.g., along the longitudinal direction LL between a
chamber of regenerator housing 310 and inlet 332 of first cap 330.
Thus, outlet 334 of first cap 330 may be cylindrical or otherwise
constant along the longitudinal direction LL in certain exemplary
embodiments.
[0082] Turning now to FIG. 14, first cap 430 of regenerator 400 has
an inlet 432 and an outlet 434, and second cap 440 has an inlet 442
and an outlet 444. The area of inlet 432 of first cap 430 may be
less than the area of outlet 434 of first cap 430, and the area of
inlet 442 of second cap 440 may be less than the area of outlet 444
of second cap 440. Outlet 434 of first cap 430 defines or includes
a plurality of channels 435 that collectively define the area of
outlet 434 of first cap 430. Channels 435 of outlet 434 of first
cap 430 extend, e.g., along the longitudinal direction LL from a
chamber of regenerator housing 410 to inlet 432 of first cap 430.
Channels 435 may also be spaced apart from one another, e.g., along
the transverse direction TT, within first cap 430. Using the
teaching disclosed herein, one of ordinary skill in the art will
appreciate that other suitable shapes and arrangements of inlets
and outlets within caps of regenerators may be provides in
alternative exemplary embodiments. For example, caps from
regenerator 200, regenerator 300 and regenerator 400 may be
combined in any suitable combination in alternative exemplary
embodiments.
[0083] This written description uses examples to disclose the
invention, including the best mode, and also to enable any person
skilled in the art to practice the invention, including making and
using any devices or systems and performing any incorporated
methods. The patentable scope of the invention is defined by the
claims, and may include other examples that occur to those skilled
in the art. Such other examples are intended to be within the scope
of the claims if they include structural elements that do not
differ from the literal language of the claims, or if they include
equivalent structural elements with insubstantial differences from
the literal languages of the claims.
* * * * *