Title of Invention

AN EXTERNAL HOUSING FOR A COLD-END ASSEMBLY OF A CRYOCOOLER AND A METHOD OF FABRICATING THE SAME

Abstract A cryocooler cold end assembly is disclosed. The assembly includes a unitary external, outer housing (201). By constructing the housing (201) from a single unitary metal shell, part count is reduced from prior art assemblies. Additionally, all brazing requirements previously necessary to secure and seal the components are eliminated. Further, due to one or more machining steps subsequent to manufacturing/forming the external sealed housing, the tolerances are improved. This allows for shrink to fit assembly of several components and also results in improved straight-line accuracy between the piston bore (152) and the displacer cylinder (120). Due to this latter improvement, the need for a displacer liner is eliminated.
Full Text This application is being filed as a PCT International Patent application on
03 December 2004, in the name of Superconductor Technologies Inc., a U.S.
national corporation, applicant for the designation of all countries except the US,
and Amr Hassan O'Baid and Mark Hanes, both U.S. citizens, applicants for the
designation of the US only, and claims priority to U.S. Application Serial No.
10/729,719, filed December 5, 2003.
FIELD OF THE INVENTION
The present invention relates generally to cryocoolers^more particularly to a
unitary cryocooler cold-end assembly housing, and still more particularly to a
unitary cold-end assembly housing which eliminates/minimizes brazing and
provides design flexibility to locate out-gassing components either internally or
externally.
BACKGROUND
, The market for superconductor products has been growing, especially in light
of a significant expanding commercial application. More specifically, high
temperature superconductor ("HTS") devices and systems have been successfully
employed in cellular communication base station filters. Such filters are designed to
reduce signal interference and increase base station sensitivity.
To operate in their intended manner, superconductor devices must generally'
be cooled to extremely low temperatures. For current HTS devices, the devices
must be cooled to about seventy-seven (77) K or lower. These cryogenic
temperatures can be reached using a cryocooler or by submersing the device to be
cooled in a fluid which boils at a low temperature. Liquids that are commonly used
to achieve cryogenic temperature are Nitrogen, which boils at seventy-seven (77) K
and Helium, which boils at four (4) K. Cryocoolers generally operate by either
controlled evaporation of volatile liquids (using the heat of vaporization as the
means to cool), by controlled expansion of gasses confined initially at high pressure
(such as 150 to 200 atmospheres), or by acting as a heat-pump by alternatively
expanding a gas near the area to be cooled (absorbing heat by the so-called heat of
expansion), then compressing the gas at another location (removing the heat by the
heat of compression) in a closed-cycle. One of the highest efficiency cryocoolers is
a closed-cycle cryocooler based upon the Stirling cycled
Stirling cycle refrigeration units (or Stirling cycle cryocoolers) typically
comprise a displacer assembly and a compressor assembly, wherein the two
assemblies are in fluid communication with one another. The assemblies are
generally driven by a prime mover. The prime mover may be implemented with an
electromagnetic linear or rotary motor.
Conventional displacer assemblies generally have a "cold" end and a "hot"
end. The hot end is in fluid communication with the compressor assembly.
Displacer assemblies generally include a displacer having a regenerator mounted
therein for displacing a fluid, such as Helium, from one end (i.e., the cold end) of the
displacer assembly to the other end (i.e., the hot end) of the displacer assembly. The
compressor assembly functions to apply additional pressure to the fluid when the
fluid is located substantially within the hot end of the displacer assembly, and to
relieve pressure from the fluid, when the fluid is located substantially within the cold
end of the displacer assembly. In this fashion, the cold end of the displacer
assembly may be maintained, for example, at seventy seven (77) K, while the hot
end of the displacer assembly is maintained, for example, at fifteen (15) degrees
above ambient temperature (e.g., at about 313 K).
¦ One of the drawbacks of current cryocoolers is the use of a large number of
components. In particular, there are a number of components that make up the
external housing. Since the device operates by compressing and expanding a fluid,
the cryocooler must be completely sealed. In practice, the various components are
brazed together in order to accomplish this requirement (e.g., to seal the cryocooler
from ambient atmosphere). However, brazing is very labor intensive. Further, the
brazing operation often introduces unwanted variances in the linearity of the
assemblies. This increases the required tolerances in the device and has lead to"
including additional component parts to accommodate the larger required tolerances
and non-linearities.
Another drawback of current cryocoolers is the inclusion of various
components into the interior of the cryocooler. Many of these components exhibit
outgassing (e.g., the diffusion of gas from the component into the internal sealed
environment of the cryocooler). Examples of components that may outgas include
the motor coil, the outer lamination, and epoxies used to bond various components
together. By introducing unwanted gasses into the internal sealed environment,
gassing often lowers the efficiency of the cryocooler.
Accordingly, there is a need in the art to develop a cryocooler with a
minimum of components forming the external sealed housing. By doing so, the
concentricity alignment between components may be improved. Further, there is a
need for design flexibility of the external sealed housing related to utilizing both
inner and outer motors. The present invention directly addresses and overcomes the
shortcomings of the prior art.
SUMMARY OF THE INVENTION
The present invention provides for an apparatus and method for improving
the tolerances and efficiency of a cryocooler cold end assembly. More.specifically,
the part count of the assembly is reduced and the labor intensive brazing and
adhering steps are eliminated. This results in an improvement in both the
manufacturing time and cost of the cryocooler. The part count is reduced in two
ways. First, the components forming the external sealed housing of the cryocooler
are minimized. Second, the cylindrical components (e.g., displacer, cylinder bore,
and piston bore) are trued to each other by machining after installation. By truing
the components, some parts can be eliminated, such as the prior art displacer
cylinder bore (displacer liner).
As discussed above, in the past brazing was often employed as the
construction method for connecting and sealing the various components. However,
the present invention preferably eliminates brazing. Further, by machining the final
critical diameters of the housing, the concentricity alignment is improved. In some
instances, bushings and other friction reducing components may be eliminated
entirely. Other components required epoxy bonding. By eliminating the need for
this type of component assembly, another source of outgassing is removed. In some
instances such as an outer design motor, outgassing components, may be moved to
the exterior of the external sealed housing. In this instance less contamination of the
internal fluid/gas environment occurs. It will be appreciated that when the desired
internal fluid/gas environment is maintained at closer to the specified levels, then the
efficiency of the cryocooler is improved.
In a preferred embodiment constructed according to the principles of the
present invention, the external sealed housing is constructed from a single unitary
metal shell. By doing so, up to ten components of prior cryocooler cold-end
assemblies are consolidated into a single part. Additionally, all brazing
requirements previously necessary to secure and seal the components are eliminated.
Further, due to one or more machining steps subsequent to manufacturing/forming
the external sealed housing, the tolerances are improved. This allows for shrink to
fit assembly of several components and also results in improved straight-line
accuracy between the piston bore and the displacer cylinder. Due to this latter
improvement, the need for a displacer liner is eliminated.
A cold-end assembly constructed in accordance with the principles of the
present invention includes a compressor and a linear motor assembly, a heat
exchanger unit, and a displacer assembly. These components are assembled and
located within the external sealed housing. A vacuum flange, an external heat
rejector, an external lamination assembly and a coil for the motor are arranged and
configured on the outside of the external sealed housing in the case of an outer
motor design embodiment. In the case of an inner motor design embodiment, only a
vacuum flange and a heat rejector are arranged and configured on the outside of the
external sealed housing. In either embodiment, by machining certain portions of the
external sealed housing and thereby improving and controlling tolerances, several of
these assemblies can be matingly seated on or within the external sealed housing in a
shrink to fit process. This process can include heating a part/assembly so that it
expands and then press fitting it into place. By correctly sizing the various parts and
assembly, when the part/assembly cools it is securely seated on or within the
external sealed housing.
A feature of the present invention is the use of a non-brazed internal heat
exchanger. The preferred heat exchanger is a readily machined or extruded
aluminum alloy. However, the heat exchanger may be constructed of any material
exhibiting good conduction properties. The prior art use of brazed fins introduced
time intensive assembly processes and necessitated increased tolerances. The
machined or extruded heat exchanger provides improved yield, thermal
management, and a.more consistent part.
Other features of the present invention include the elimination of electrical
feed-throughs in the external sealed housing for the outer motor embodiment, the
optional utilization of a flexure bearing, a gas bearing or other bearing designs, and
the optional utilization of a moving coil motor, a moving magnet motor, or other
motor designs.
In the case of the optional gas bearings, such bearings preferably use the
working fluid to reduce and ideally eliminate friction between the piston and the
cylinder comprising the compressor. To implement the gas bearings, pressurized
gas may be passed through a check valve into a sealed interior of the piston. This
provides a source of pressurized gas for the gas bearing that does not fluctuate
significantly with the pressure of any gas that resides hi the compression chamber of
the compressor assembly. Other cryocooler designs utilize lubricants that influence
the working fluid purity or rubbing surfaces that influence the operating life
capacity.
Therefore, according to one aspect of the invention, there is provided, an
external housing for a cold-end assembly of a cryocooler, of the type including'a
heat exchanger, a displacer cylinder assembly and a displacer cylinder primary
mover, the external housing comprising: a substantially unitary housing arranged
and configured to house the heat exchanger, the displacer cylinder assembly and at
least a portion of the displacer cylinder primary mover. Another aspect of the
invention includes the preceding housing and further comprising a first section
arranged and configured to act as a cold finger and to substantially house the
displacer cylinder assembly; a second section arranged and configured to
substantially house a heat exchanger; and a third section arranged and configured to
substantially house at least a portion of the displacer cylinder primary mover.
According to another aspect there is provided a housing for a cold-end
assembly of a cryocooler, of the type that includes a heat exchanger, a displacer
cylinder assembly and a displacer cylinder primary mover, comprising: a first
section arranged and configured to act as a cold finger and to substantially house the
displacer cylinder assembly; a second section arranged and configured to
substantially house a heat exchanger; and a third section arranged and configured to
substantially house at least a portion of the displacer cylinder primary mover; and
wherein at least two of the first section, second section and third section are
seamlessly connected to one another.
According to yet another aspect of the invention, there is provided, a cold
end assembly, of the type used to compress a fluid at a hot end and deliver a cooled
fluid to a cold end, comprising: a primary mover; a displacer cylinder operatively
connected to the primary mover for compressing; a heat exchanger; and a
substantially seamless and/or unitary housing arranged and configured to support
and substantially enclose the displacer cylinder and the heat exchanger, and to
support and enclose at least a portion of the primary mover.
Yet another aspect of the invention includes a method of fabricating a cold
end assembly for a cryocooler, comprising: drawing a unitary housing for the cold
end assembly; machining at least one selected internal diameter of the housing;
installing a piston bore assembly proximate to at least one of the machined internal
diameters; machining at least one selected external diameter of the housing; and
installing a vacuum flange proximate to at least one of the selected external
diameters.
While the invention will be described with respect to the preferred
embodiment configurations and with respect to particular devices used therein, it
will be understood that the invention is not to be construed as limited in any manner
by either such configuration or components described herein. Also, while the
particular shape and unitary nature of the sealed external housing are described
herein, it will be understood that such particular shape and unitary structure is not to
be construed in a limiting manner. Instead, the principles of this invention extend to
minimizing the number of components to construct the sealed external housing so as
to eliminate brazing and/or improve tolerances. Further, while the preferred
embodiment(s) of the invention will be generally described in relation to use of the
cryocooler in a cellular base station environment, it will be understood that the scope
of the invention is not to be so limited. These and other variations of the invention
will become apparent to those skilled in the art upon a more detailed description of
the invention.
The advantages and features, which characterize the invention, are pointed
out with particularity in the claims annexed hereto and forming a part hereof. For a
better understanding of the invention, however, reference should be had to the
drawings which form a part hereof and to the accompanying descriptive matter, in
which there is illustrated and described a preferred embodiment of the invention.
BRIEF DESCRIPTION OF THE DRAWINGS
Referring to the drawings, wherein like numerals represent like parts
throughout the several views:
FIG. 1 is a cross sectional illustration of a prior art cold end assembly.
FIG. 2a is a cross sectional illustration of the external components of the cold
end assembly of FIG. 1.
FIG. 2b is a cross sectional illustration of the various components of the cold
end assembly of FIG. 1 that are replaced by components in an embodiment of the
present invention constructed in accordance with the principles of the present
invention.
FIG. 3 is a cross-sectional illustration of a cold end assembly constructed in
accordance with the principles of the present invention, wherein the motor is located
partially external to the sealed external chamber.
FIG. 4 is a perspective view of a sealed external chamber "of Fig. 3.
FIGS. 5a-5f are a series of cross-section illustrations for machining and
assembling of a cold end assembly constructed in accordance with the principles of
the present invention.
FIG. 6 is a cross-sectional illustration of an alternative embodiment cold end
assembly constructed in accordance with the principles of the present invention,
wherein the motor is located internal to the sealed external chamber.
FIGS. 7a-7f are a series of cross-section illustrations for machining and
assembling of the alternative embodiment cold end assembly of FIG. 6.
DETAILED DESCRIPTION
A cryocooler including a cold-end assembly constructed in accordance with
the principles of the present invention may be employed in a variety of environments
and with a variety of other components. However, the principles apply to a method
and apparatus for improving the tolerances and efficiency of a cryocooler cold end
assembly. The improvements are realized by minimizing the components forming
the external sealed housing of the cryocooler and by optionally locating out-gassing
components to the exterior of the external sealed housing.
A discussion of the preferred embodiment cold-end assembly will be
deferred pending a discussion of a prior art cold-end assembly shown in FIG. 1. A
representative prior art Stirling cycle cryocooler 10 is illustrated. The cryocooler 10
is described in more detail in U.S. Patent No. 6,327,862, titled STIRLING CYCLE
CRYOCOOLER WITH OPTIMIZED COLD END DESIGN, and assigned to the
assignee of the present invention. Such patent is incorporated herein and made a
part hereof. Accordingly, not all of the components or the operation of the
cryocooler will be discussed herein. The cryocooler 10 of FIG. 1 generally includes
a displacer unit 12, a heat exchanger unit 14, and a compressor and linear motor
assembly 16.
The displacer unit 12 functions in a conventional manner and preferably
includes a displacer housing 18, a displacer cylinder assembly 20 having a
regenerator unit 22 mounted therein, and a displacer rod assembly 24. The displacer
cylinder assembly 20 is slideably mounted in the axial direction (i.e., the Z axis)
within the displacer housing 18 and rests against the displacer liner that is affixed to
the inner surface of the displacer housing 18. A displacer end cap 27 is provided
within a distal end of the displacer cylinder assembly 20. The displacer rod
assembly 24 is connected at one end to the displacer cylinder assembly 20 and
coupled at the other end 34 to a displacer flexure spring assembly 32. Thus, under
appropriate conditions, it is possible for the displacer cylinder assembly 20 to
oscillate within the displacer housing 18.
The heat exchanger unit 14 is located between the displacer unit 12 and the
compressor and linear motor assembly 16. The heat exchanger unit includes a heat
exchanger block 38, a flow diverter or equivalent structure, and a heat exchanger
mounting flange 42. The heat exchanger mounting flange 42 is coupled to a distal
end of a pressure housing 44 of the compressor and linear motor assembly 16. The
heat exchanger block 38 includes a plurality of internal heat exchanger fins 46 and a
plurality of external heat rejector fins 48. Thus, the heat exchanger unit 14 is,
designed to facilitate heat dissipation from a gas, such as Helium, that is compressed
in the region located at the juncture between the displacer unit 12 and the
compressor and linear motor assembly 16 (this region, Phot, may also be referred to
as the compression chamber of the compressor and linear motor assembly 16). The
heat exchanger block 38, internal heat exchanger fins 46 and external heat rejector
fins 48 are generally made from high purity copper.
The compressor and linear motor assembly 16 include a pressure housing 44
that has a piston assembly 50 mounted therein. The piston assembly 50 includes a
cylinder 52, a piston 54, a piston assembly mounting bracket 56 and a spring
assembly 58. The piston assembly mounting bracket 56 provides a coupling
between the piston 54 and the spring assembly 58, and the piston 54 is adapted for
reciprocating motion within the cylinder 52. A plurality of gas bearings 60 is
provided within the exterior wall 62 of the piston 54, and the gas bearings 60 receive
gas, e.g., Helium, from a sealed cavity 61 that is provided within the piston 54. A
check valve 63 provides a unidirectional fluid communication conduit between the
sealed cavity 61 and the compression chamber of the cylinder (e.g., the area
designated Phot) when the pressure of the gas within that region exceeds the
pressure within the cavity 61 (i.e., exceeds the piston reservoir pressure).
The piston 54 preferably has mounted thereon a plurality of magnets 74.
Internal laminations 72 are secured to the outside of the cylinder 52. External
laminations 73 are secured within the pressure housing 44 and are located outward
of the magnets 74. The external laminations 73 are preferably secured to a mounting
flange 42. The internal and external laminations 72,73 are preferably made of an
iron-containing material. A motor coil 70 preferably lies within the external
laminations 73 and surrounds the piston 54. The motor coil 70 is preferably located
outward of the magnets 74 and within recesses formed within the external
laminations 73. Thus, it will be appreciated that, as the piston 54 moves within the
cylinder 52, the magnets 74 move within a gap 75.
It will be appreciated from the foregoing that a number of components make
up the external sealed housing. FIG. 2a illustrates the various components making
up the external sealed housing in more detail. Brazing is utilized to bond and seal a
number of the various components to one another. Still further, there are a number
of components that are assembled using various epoxy bonds.
Turning now to FIG. 3, a cross section view of a cold-end cryocooler
assembly constructed in accordance with the principles of the present invention is
illustrated. The cryocooler is designated at 100 and generally includes an external
sealed housing 201 that provides structural support for the various components, parts
and assemblies of the cold-end assembly. The major assemblies of the cold-end
assembly include a displacer unit 112, a heat exchanger unit 114, and a compressor
and linear motor assembly 116. The linear motor assembly acts as the prime mover
for the compressor. Each of the assemblies will be discussed in greater detail below.
FIG. 4 illustrates the external sealed housing 201 in a perspective view. FIG.
5a illustrates the external sealed housing 201 in cross section. From FIGS. 4 and 5a,
it will be appreciated that the housing 201 is a unitary construction of "stainless steel
304." Such material is a widely used stainless steel, and generally has a content of
about 18 and 8 percent chromium and nickel content, respectively. The material
provides a good combination of strength and corrosion resistance, as well as
providing good fabrication characteristics. The material is resistant to a wide range
of environments between moderately reducing and slightly oxidizing. In the present
case, it forms the material for housing 201 that seals the Helium internal atmosphere.
The material also offers appropriate structural support for the various subassemblies.
In the preferred embodiment, the material is drawn from a starting disk of sheet
metal approximately eight and three-quarters inch (8 and 3/4") diameter. After
being drawn, in a preferred embodiment, the final largest outside diameter is
approximately 3.442" diameter and the housing 201 has an approximate height of
8.546".
Other materials exhibiting the necessary properties for housing 201 include
Titanium, Inconel or Cobalt. Other materials might also be utilized. The desirable
characteristics of the materials include structural stability, low thermal conduction,
high permeability resistance and material properties, which allow welding and
machining.
Still referring to FIGS. 4 and 5a, the housing 201 includes several sections
that are arranged and configured to support and/or house different sub-assemblies. It
will be appreciated that the housing 201, in addition to its structural support and
sealing functions, also provides other functions moving from a closed, first end 213
of the housing 201 to an open, second end 214 of the housing 201. The closed end
214 of the housing 201 may be kept open to simplify the final machining sequence
for alignment, but it is required to finally close it by welding, brazing, epoxying or
any hermetic thermal shock resistant procedure.
First section 215 is located at the end closest to first end 213. First section
215 is arranged and configured to act as a cold finger about its exterior. In the
preferred embodiment, first section 215 extends through the vacuum flange 200
(e.g., see FIG. 3). The HTS filters (not shown) are subsequently attached to a
mounting bracket 252 (best seen in FIG. 3) at, or proximate to, first end 213. First
section 215 is also arranged and configured to house regenerator unit 122 (best seen
in FIG. 3). First section 215 is preferably round and, in the preferred embodiment,
has a smaller diameter than the other sections of the housing 201.
Second section 217 is located next to first section 215, with first transition
section 216 located therebetween. Vacuum flange 200 is mounted on the exterior of
second section 217. Preferably, the vacuum flange 200 is mounted via a shrink to fit
process. Accordingly, the exterior of the second section 217 is preferably machined
to an appropriate diameter (with a controlled tolerance) to accomplish this
connection. As will be appreciated, the connection between the vacuum flange 200
and second section 217 provides a seal for the vacuum environment into which the
cold finger (e.g., the first section 215) extends. The interior of second section 217
generally cooperates with and supports heat exchanger unit 114. The second section
217 is preferably round and, in the preferred embodiment has a larger diameter than
first section 215.
Third section 219 is located next to second section 217, with second
transition section 218 located therebetween. On the exterior of third section 219, the
coil 170 and the external laminations 204 are supported. The interior of third section
219 generally cooperates with and supports the internal components of the linear
motor 116. The third section 219 is preferably round and, in the preferred
embodiment has a larger diameter than second section 217.
Fourth section 221 is located next to third section 219, with third transition
section 220 located therebetween. Fourth section 221 is located at or near open,
second end 214. Fourth section 221 supports the spring assembly for the displacer
assembly. It also sealingly engages with an end cap 250 (best seen in FIG. 3) to seal
the cold end assembly. The fourth section 221 is preferably generally frusto-conical
in shape. In the preferred embodiment the smaller end of the fourth section 221 has
a larger diameter than third section 219.
As noted above, each of the sections 215,217,219 and 221 are preferably
drawn to form a unitary and seamless housing 201. However, it will be appreciated
that the individual sections might optionally be drawn as two or more component
pieces and then subsequently assembled. While this optional method of
manufacturing may be employed, in order to minimize the number of seams and
improve the manufacturing processes of the cold-end assembly 100," it is preferred to
draw the entire housing 201 in a single process.
It will also be appreciated that the first end 213 has been characterized as
being closed, while the second end 214 has been characterized as being open. Such
characterizations, however, should not be construed in a limiting manner. In the
preferred embodiment, the second end 214 is open to enable assembly. However, if
the housing 201 is manufactured in two or more component pieces (e.g., providing
for a seam at transition section 218 and/or 220), then the second end 214 may be
constructed in a closed fashion. Still further, it will be appreciated that the transition
sections 216,218 and 220 may optionally be eliminated and/or take on a number of I
shapes and configurations. The main function of such sections is to provide a
transition between functional sections of the housing 201.
FIGS. 5a - 5f illustrate the various machining steps which preferably occur
subsequent to the drawing process. At FIG. 5a, the internal surfaces of housing 201
have been manually honed and the inside diameters are machined at locations 301,
303, and 305. At FIG. 5b, the inner piston bore assembly 307, the heat exchanger
block 309 and the spring stack mounting support 308 is inserted into the housing
201. At FIG. 5c, the exterior of housing 201 is machined at locations 311 (to reduce
the thermal conduction path through the external housing material thickness), 313
(to produce a suitable dimension for a tight shrink fit connection), and 315 (to
reduce the Eddy current loss path only for the external motor design ~ this
machming step is not necessary for an internal motor design as described in
connection with the alternative embodiment described below). These three locations
311, 313, and 315 generally correspond with first section 215, second section 217/
and third section 219, respectively. At FIG. 5d, the vacuum flange 200 is preferably
shrink fit onto housing 201 by heating the flange 200 and press fitting it into place.
At FIG. 5e, the vacuum flange 200 surface designated by 317 is machined. This
surface 317 will receive the external heat rejector 148 (best seen in Fig. 3). Finally
at FIG. 5f, three more internal surfaces are machined. These three surfaces are
designated at 319, 321 and 323. These last machining operations help maximize the
alignment between the piston, compressor, and displacement assemblies. It will be
appreciated that the components illustrated in FIG. 5f take the place of the prior art
components shown in FIG. 2b.
By machining the components as described in connection with Figs. 5a-5f
above, the concentricity alignment of the components is improved. For example, in
the prior art, the concentricity may have been approximately .0015". However, by
constructing the housing 201 as described herein, the overall concentricity is
improved to about .0007". This improvement in concentricity improves other
tolerances, makes assembly easier, and provides for greater consistency in the
manufacturing process.
Returning now to FIG. 3 a brief discussion will be presented describing an
assembled cold-end assembly 100. The displacer unit 112 functions in a manner
known to those of skill in the art and preferably includes a displacer housing 118, a
displacer cylinder assembly 120 having a regenerator unit 122 mounted therein, and
a displacer rod assembly 124. The displacer cylinder assembly 120 is slideably
mounted within the displacer housing 118. A displacer end cap 127 is provided
within a distal end of the displacer cylinder assembly 120. The displacer rod
assembly 124 is coupled at a first end to a base section (not shown) of the displacer
cylinder assembly 120 and coupled at the second end 134 to a displacer flexure
spring assembly 132. Therefore, given the appropriate conditions, the displacer
cylinder assembly 120 oscillates within the displacer housing 118. Due to the
improved tolerances and in-line accuracy between the displacer cylinder assembly
120 and the piston bore, there is no need for the displacer liner as required in the
prior art.
Still referring to Fig. 3, the heat exchanger unit 114 is located between the
displacer unit 112 and the compressor and linear motor assembly 116. The heat
exchanger unit includes a heat exchanger block 309 and a plurality of external heat
rejector fins 148. Thus, the heat exchanger unit 114 is designed to facilitate heat
dissipation from a gas, such as Helium, that is compressed in the region located at
the juncture between the displacer unit 112 and the compressor and linear motor
assembly 116 (i.e., the compression chamber, Phot)- Preferably the heat exchanger
block 309 is constructed of a high purity copper and is installed as a component
within the housing 201 (described above). Preferably, the external heat rejector fins
148 are also made from high purity copper. Other materials exhibiting good thermal
conduction characteristics might also be used. Due to the shrink to fit coupling of
the vacuum flange 200 to the sealed chamber 201, there is no need for a heat
exchanger mounting flange as in the prior art.
The compressor and linear motor assembly 116 are mounted within sealed
chamber 201 and include a piston assembly 150. The piston assembly 150 includes
a cylinder 152, a piston 154, a piston assembly mounting bracket 155 and a spring
assembly 156. The piston assembly mounting bracket 155 provides a coupling
between the piston 154 and the spring assembly 156. Piston 154 is adapted for
reciprocating motion within the cylinder 152. One or more gas bearings 160 are
provided within the exterior wall of the piston 154. The gas bearings 160 receive
gas, e.g., Helium, from a sealed cavity 162. A check valve 163 provides a
unidirectional fluid communication conduit between the sealed cavity 162 and the
compression chamber of the cylinder (e.g., the area designated Phot) when the
pressure of the gas within that region exceeds the pressure within the cavity 162
(i.e., exceeds the piston reservoir pressure).
The linear motor assembly 116 includes a plurality of external coils 170 and
externally located outer laminations 204. The internal laminations 208 are mounted
on the inner piston bore assembly 307. Moving magnets 210 are located beneath the
coil 170, with the sealed chamber 201 located therebetween. Thus, it will be
appreciated that, as the piston 154 moves within the cylinder 152, the moving
internal magnets 210 also move.
Other types and styles of motors may optionally be utilized in the cold end
assembly 100. For example, motor assembly 116 may be modified to include the
motor designs of U.S. Patent Nos. 4,602,174; 6,141,971; 6,427,450; and 6,483,207.
In Operation
During operation, the piston 154 and displacer cylinder assembly 120
generally oscillate at a resonant frequency of approximately 60 Hz and in such a
maimer that the oscillation of the displacer cylinder assembly 120 is approximately
90 degrees out of phase with the oscillation of the piston 154. It will be appreciated
that this means that the motion of the displacer cylinder assembly 120 "leads" the
motion of the piston 154 by approximately 90 degrees.
Those skilled in the art will appreciate that, when the displacer cylinder
assembly 120 moves to the "cold" end of the displacer housing 118, most of the
fluid, e.g. Helium, within the system is displaced to the warm end of the displacer
housing 118 and/or moves around a flow diverter or similar structure and through
the internal heat exchanger fins into the compression area of piston assembly 150.
Due to the phase difference between the motion of the displacer cylinder assembly
120 and the piston 154, the piston 154 should be at mid-stroke and moving in a '
direction toward the flow diverter 140 when displacer cylinder assembly 120 is
located at the cold end of the displacer housing 118. This causes the Helium in the
area to be compressed, thus raising the temperature of the Helium. The heat of
compression is transferred from the compressed Helium to the internal heat
exchanger fins and from there to the heat exchanger block 309 and external heat
rejector fins 148. From the heat rejector fins 148, the heat is transferred to ambient
air. As the displacer assembly 120 moves to the warm end of the displacer housing
118, the Helium is displaced to the cold end of the displacer housing 118. As the
Helium passes through the displacer cylinder 120, it deposits heat within the
regenerator 122, and exits into the cold end of the displacer housing 118 at .
approximately 77 K. At this time, the compressor piston 154 preferably is at mid-
stroke and moving in the direction of the piston flexure springs 156. This causes the
Helium in the cold end of the displacer housing 118 to expand further reducing the
temperature of the Helium and allowing the Helium to absorb heat. In this fashion,
the cold end functions as a refrigeration unit and may act as a "cold" source.
Alternative Embodiment
FIG. 6 illustrates a cross section view of an alternative embodiment design
constructed in accordance with the principles of the invention. The alternative
embodiment includes an inner motor design or arrangement. More specifically, all
of the components of the linear motor assembly 116' are located internally within the
external sealed housing 201'. Other than the location of various components of the
linear motor assembly 116' and the shape of the sealed housing 201', the other
components and operation of the cryocooler 100' remain the same. It will be
appreciated that the various components and the operation of the cryocooler 100'
have been described in detail above in connection with cryocooler 100.
Accordingly, such components will not be described in detail in connection with the
alternative embodiment. However, a discussion of the external sealed housing 201'
follows.
FIGS. 7a-7f illustrate the various machining steps which preferably occur
subsequent to the drawing process of the housing 201'. At FIG. 7a, the internal
surfaces of housing 201' have been manually honed and the inside diameters are
machined at locations 301,303', and 305'. It will be appreciated that due to locating
parts of the linear motor assembly 116' within the housing 201', the diameter of the
third section 219' is larger than third section 219 of housing 201 described above.
Similarly, transition section 218' is changed so as to transition between second
section 217 and third section 219'. Further, due to the larger circumference of
section 219', transition section 220 may be eliminated. Instead, frusto-conical
shaped fourth section 221' may immediately be connected to third section 219'. It
will further be appreciated that due to the increased diameter of third section 219'
and the shape of fourth section 221', the corresponding machined locations in the
alternative embodiment are designated 303' and 305', respectively. However, such
locations are machined for similar purposes as locations 303 and 305 above.
At FIG. 7b, the inner piston bore assembly 307 is inserted into the housing
201'. Also inserted into housing 201' is heat exchanger block 309 and the spring
stack mounting support 308. At FIG. 7c, the exterior of housing 201' is machined at
locations 311 (to reduce the thermal conduction path through the external housing
material thickness), 313 (to produce a suitable dimension for a tight shrink fit
connection) and, optionally, 315' (as noted above, this location does not have to be
machined" in the instance of an internal motor configuration). These locations
generally correspond with first section 215, second section 217, and third section
219', respectively. At FIG. 7d, the vacuum flange 200 is preferably shrink fit onto
housing 201' by heating the flange 200 and press fitting it into place. At FIG. 7e, the
vacuum flange 200 surface designated by 317 is machined. This surface 317 will
receive the external heat rejector fins 148. Finally at FIG. 7f, three more internal
surfaces are machined. These three surfaces are designated at 319, 321 and 323.
These last machining operations help maximize the alignment between the piston,
compressor, and displacement assemblies. It will be appreciated that the
components illustrated in FIG. 7f take the place of the prior art components shown
in FIG. 2b.
While particular embodiments of the invention have been described with
respect to its application, it will be understood by those skilled in the art that the
invention is not limited by such application or embodiment or the particular
components disclosed and described herein. It will be appreciated by those skilled
in the art that other components that embody the principles of this invention and
WE CLAIM
1. An external housing for a cold-end assembly of a cryocooler including a heat exchanger, a
displacer cylinder assembly and a displacer cylinder primary mover, the external housing
comprising: a unitary one-piece housing arranged and configured to house the heat exchanger,
the displacer cylinder assembly and at least a portion of the displacer cylinder primary mover.
2. The housing as claimed in claim 1, wherein the unitary housing comprises a first section
arranged and configured to act as a cold finger and to house the displacer cylinder assembly; a
second section arranged and configured to house a heat exchanger; and a third section arranged
and configured to house at least a portion of the displacer cylinder primary mover.
3. The housing as claimed in claim 2, further comprising a fourth section arranged and
configured to cooperatively attach to an end cap.
4. The housing as claimed in claim 2, wherein the second section is further arranged and
configured to matingly engage a vacuum flange.
5. The housing as claimed in claim 4, wherein the combination of the second section and the
vacuum flange is arranged and configured to provide structural support for a heat rejector located
about the periphery of the vacuum flange.
6. The housing as claimed in claim 5, wherein the first section, the second section and the third
section each have a round cross section.
7. The housing as claimed in claim 6, wherein the second section has a larger cross section than
the first section and the third section has a larger cross section than the second section.
8. The housing as claimed in claim 2, wherein the first section is seamlessly connected to the
second section with a first transition section.
9. The housing as claimed in claim 2, wherein the second section is seamlessly connected to the
third section with a second transition section.
10. The housing as claimed in claim 3, wherein the third section is seamlessly connected to the
fourth section with a third transition section.
11. The housing as claimed in claim 3, wherein: a) the first section is seamlessly connected to
the second section with a first transition section; b) the second section is seamlessly connected to
the third section with a second transition section; and c) the third section is seamlessly connected
to the fourth section with a third transition section.
12. A housing for a cryocooler that includes a heat exchanger, a displacer cylinder assembly and
a displacer cylinder primary mover, comprising: a) a first section arranged and configured to act
as a cold finger and to house at least a portion of the displacer cylinder assembly; b) a second
section arranged and configured to house a heat exchanger; and c) a third section arranged and
configured to house at least a portion of the displacer cylinder primary mover; and wherein, at
least two of the first section, second section and third section have different diameters from each
other and are seamlessly connected to one another.
13. The housing as claimed in claim 12, wherein the first section is seamlessly connected to the
second section and the second section is seamlessly connected to the third section.
14. The housing as claimed in claim 13, further comprising: a) a first transition section between
the first section and the second section; and b) a second transition section between the second
and third sections.
15. A cryocooler, of the type used to compress a fluid at a hot end and deliver a cooled fluid to a
cold end, comprising: a) a primary mover; b) a displacer cylinder operatively connected to the
primary mover for compressing;: c) a heat exchanger; and d) a housing comprising a seamless
housing portion arranged and configured to support and enclose at least a portion of the displacer
cylinder, at least a portion of the heat exchanger, and at least a portion of the primary mover.
16. The cold end assembly as claimed in claim 15, wherein the housing portion is entirely
seamless from a first end to a second end, and wherein the housing is closed at the first end and
open at the second end during an assembly stage.
17. The cold end assembly as claimed in claim 16, further comprising an end cap, the end cap
sealing engaging the second end of the housing.
18. A Stirling cycle cryocooler, comprising: a) a displacer unit; b) a heat exchanger unit,
c) a compressor and linear motor assembly; and d) a sealed housing, wherein the housing is
arranged and configured to support and enclose at least portions of the displacer unit, the heat
exchanger, and the compressor and linear motor assembly.
19. The cryocooler as claimed in claim 18, wherein the housing portion is entirely seamless
from a first end to a second end, and wherein the housing is closed at the first end and open at the
second end during an assembly stage.
20. The cryocooler as claimed in claim 19, further comprising an end cap, the end cap sealing
engaging the second end of the housing portion.
21. A method of fabricating a housing for a cryocooler, comprising: a) drawing a unitary
portion of an external housing for the cryocooler; b) machining at least one selected internal
diameter of the housing; c) installing a piston bore assembly proximate at least one of the
machined internal diameters; d) machining at least one selected external diameter of the housing;
and e) installing a vacuum flange proximate at least one of the selected external diameters.
22. The external housing as claimed in claim 2, wherein at least two of the first, second and third
section have different diameters from each other.
23. An external housing of a cryocooler, of the type including a heat exchanger, a displacer
cylinder assembly and a displacer cylinder primary mover arranged along an axis, the external
housing comprising:
a unitary one-piece tubular housing portion arranged and configured to surround at least a
portion of the heat exchanger, at least a portion of the displacer cylinder assembly and at least a
portion as claimed in the displacer cylinder primary mover about the axis.
24. The external housing as claimed in claim 23, wherein the unitary one-piece tubular housing
portion is arranged and configured to surround the heat exchanger, the displacer cylinder
assembly and at least a portion of the displacer cylinder primary mover about the axis.
25. The external housing as claimed in claim 23, wherein the tubular housing portion defines a
housing axis and comprises at least two sections disposed along the housing axis, the two
sections having different internal cross-sectional areas from each other.
26. The external housing as claimed in claim 25, wherein the tubular housing portion comprises
at least three sections disposed along the axis, the sections having successively greater internal
cross-sectional areas along the axis.
27. The external housing as claimed in claim 23, wherein the tubular housing portion is further
arranged and configured to surround at least a portion of at least a portion of a compressor of the
cryocooler about the axis.


A cryocooler cold end assembly is disclosed. The assembly includes a unitary external, outer
housing (201). By constructing the housing (201) from a single unitary metal shell, part count
is reduced from prior art assemblies. Additionally, all brazing requirements previously
necessary to secure and seal the components are eliminated. Further, due to one or more
machining steps subsequent to manufacturing/forming the external sealed housing, the
tolerances are improved. This allows for shrink to fit assembly of several components and
also results in improved straight-line accuracy between the piston bore (152) and the displacer
cylinder (120). Due to this latter improvement, the need for a displacer liner is eliminated.

Documents:

01847-kolnp-2006-absttract.pdf

01847-kolnp-2006-assignment.pdf

01847-kolnp-2006-claims.pdf

01847-kolnp-2006-correspondence others.pdf

01847-kolnp-2006-description(complete).pdf

01847-kolnp-2006-drawings.pdf

01847-kolnp-2006-form-1-1.1.pdf

01847-kolnp-2006-form-1.pdf

01847-kolnp-2006-form-2.pdf

01847-kolnp-2006-form-3.pdf

01847-kolnp-2006-form-5.pdf

01847-kolnp-2006-pct form.pdf

01847-kolnp-2006-priority document.pdf

01847-kolnp-international publication.pdf

01847-kolnp-international search authority report.pdf

1847-KOLNP-2006-ABSTRACT.pdf

1847-KOLNP-2006-CANCELLED DOCUMENT.pdf

1847-KOLNP-2006-CLAIMS.pdf

1847-KOLNP-2006-CORRESPONDENCE.pdf

1847-KOLNP-2006-DESCRIPTION COMPLETE.pdf

1847-KOLNP-2006-DRAWINGS.pdf

1847-KOLNP-2006-FORM 1.pdf

1847-KOLNP-2006-FORM 13.pdf

1847-KOLNP-2006-FORM 2.pdf

1847-KOLNP-2006-FORM 3.pdf

1847-kolnp-2006-granted-abstract.pdf

1847-kolnp-2006-granted-claims.pdf

1847-kolnp-2006-granted-correspondence.pdf

1847-kolnp-2006-granted-description (complete).pdf

1847-kolnp-2006-granted-drawings.pdf

1847-kolnp-2006-granted-examination report.pdf

1847-kolnp-2006-granted-form 1.pdf

1847-kolnp-2006-granted-form 13.pdf

1847-kolnp-2006-granted-form 18.pdf

1847-kolnp-2006-granted-form 2.pdf

1847-kolnp-2006-granted-form 3.pdf

1847-kolnp-2006-granted-form 5.pdf

1847-kolnp-2006-granted-pa.pdf

1847-kolnp-2006-granted-reply to examination report.pdf

1847-kolnp-2006-granted-specification.pdf

1847-KOLNP-2006-REPLY FIRST EXAMINATION REPORT.pdf

1847-KOLNP-2006-REPLY TO EXAMINATION REPORT.pdf

abstract-01847-kolnp-2006.jpg


Patent Number 241945
Indian Patent Application Number 1847/KOLNP/2006
PG Journal Number 34/2010
Publication Date 20-Aug-2010
Grant Date 02-Aug-2010
Date of Filing 03-Jul-2006
Name of Patentee SUPERCONDUCTOR TECHNOLOGIES INC.
Applicant Address 460 WARD DRIVE, SANTA BARBARA, CA
Inventors:
# Inventor's Name Inventor's Address
1 O'BAID, AMR HASSAN 450 WHITMAN STREET, APARTMENT 61, GOLETA, CALIFORNIA 93117
2 HANES, MARK 658, SANTA MARGUERITA DRIVE, GOLETA, CALIFORNIA 93117
PCT International Classification Number F25B 9/14
PCT International Application Number PCT/US2004/040399
PCT International Filing date 2004-12-03
PCT Conventions:
# PCT Application Number Date of Convention Priority Country
1 10/729,719 2003-12-05 U.S.A.