US3302422A - Refrigeration apparatus - Google Patents

Refrigeration apparatus Download PDF

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Publication number
US3302422A
US3302422A US357902A US35790264A US3302422A US 3302422 A US3302422 A US 3302422A US 357902 A US357902 A US 357902A US 35790264 A US35790264 A US 35790264A US 3302422 A US3302422 A US 3302422A
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gas
tube
tubular member
chamber
refrigeration
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US357902A
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English (en)
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Howard John Treweek Smith
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Petrocarbon Developments Ltd
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Petrocarbon Developments Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C3/00—Vessels not under pressure
    • F17C3/02—Vessels not under pressure with provision for thermal insulation
    • F17C3/08—Vessels not under pressure with provision for thermal insulation by vacuum spaces, e.g. Dewar flask
    • F17C3/085—Cryostats
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/004—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being air
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F6/00—Superconducting magnets; Superconducting coils
    • H01F6/04—Cooling

Definitions

  • Refrigeration at low temperatures of the order of 200 K. and down to very low temperatures of the order of K. is required in small quantities, for an increasing number of scientific purposes, for example, for use in connection with infrared detectors, masers and cryotrons.
  • the usual methods of .producing refrigeration for these purposes are either by expansion using a piston expansion device or by expansion through a Joule-Thomson valve.
  • the first method has the disadvantage that it involves parts moving at low temperatures, while the second method has the disadvantages that it involves very high pressures, of about 2,000 pounds per square inch and that, if it is to be operated in more than one stage, different working gases are usually required in the several stages.
  • the present invention includes refrigeration apparatus comprising a tubular member which is open at one end and closed at the other end, a thermal regenerator in communication with the open end of the tubular member, a gas conduit in communication with the thermal regenerator so that gas under pressure may be passed from the gas conduit through the thermal regenerator to the tubular member and exhausted with expansion from the tubular member through the thermal regenerator to the gas conduit, the thermal regenerator serving to abstract heat from gas entering the tubular member and return heat to gas leaving the tubular member, valve means in said gas conduit for controlling the flow of gas to and from the tubular member and arranged to permit the gas to enter and leave the tubular member as a succession of charges and heat exchange means adjacent the closed end of the tubular member for enabling a coolant to be passed in thermal contact with the tubular member adjacent to the closed end thereof, whereby on operation of the apparatus with gas under pressure being fed into, and exhausted with expansion from, the tubular member as a succession of charges and with a coolant passing through the said heat exchange means refrigeration is made available near the open end of the tub
  • the present invention includes also a method of producing refrigeration which comprises repeatedly perform ing the cycle of admitting compressed gas to a relatively long and narrow chamber through an inlet situated at one end thereof, with abstraction of heat from the gas before it enters the chamber abstracting heat from the chamber near the end thereof remote from the inlet, and exhausting compressed gas from the chamber with expansion thereof within the chamber and with return of abstracted heat to the gas after it leaves the chamber,
  • the invention includes further a unit for use in refrigeration apparatus, comprising a tube open at one end and closed at the other end, heat exchange means secured to the tube in thermal contact therewith adjacent its closed end, a housing with an opening at each end secured to the tube in communication with the open end of the tube and heatabsorbing packing within the housing for abstracting heat from gas entering the tube and for delivering heat to gas leaving the tube.
  • FIGURE 1 is a diagrammatic view of a single stage refrigeration apparatus according to the invention.
  • FIGURE 2 is a longitudinal section through a part of the apparatus shown in FIGURE 1;
  • FIGURE 3 is a longitudinal section through part of a two-stage refrigeration apparatus according to the invention.
  • FIGURE 4 is a cross-section on the line 1VIV of FIGURE 3.
  • FIGURE 5 is a diagram of the valve timings adopted and pressure changes occurring in a typical operation of the apparatus illustrated in FIGURES 1 and 2 and in FIGURE 3.
  • FIGURE 6 is a schematic view of a three-stage refrigeration apparatus in accordance with the invention.
  • the refrigeration apparatus includes an elongated tube 10, which is closed at its end 11 and communicates at its other end with a thermal regenerator 12.
  • a first heat exchange means 13, through which a coolant fluid may be circulated by connecting pipes 14, 15 is secured to the tube 10 near its closed end 11 in thermal contact therewith.
  • a second heat exchange means 16 is similarly secured to the pipe 10 adjacent the thermal regenerator 12 and is provided with connecting pipes 17, 18 for circulating a fluid to be used as a refrigerant therethrough.
  • thermal regenerator 12 and heat exchange means 13 and 16 are encased within a thermal insulating box 19 which may be packed with insulating material or be under high vacuum.
  • the thermal regenerator 12 communicates via pipe 20 with a pipe line 21 communicating at one end with the outlet 22 and at its other end with the inlet 23 of a gas compressor 24.
  • An after-cooler 25 is provided on the outlet side of compressor 24 to remove heat of compression from gas compressed 'by the compressor.
  • An inlet valve 26 arranged to be operated *by a solenoid 27 to move from the fully open to the fully closed position and vice versa is set in gas line 21 and between compressor outlet 22 and tube 10, while an outlet valve 28 also arranged to be operated by a solenoid 2? to move from the fully open to the fully closed position and vice versa is set in gas line 21 and between tube 10 and compressor inlet 23.
  • a gas reservoir 31 is included in line 21 between compressor outlet 22 and inlet valve 26, while a further gas reservoir 32 is included in line 21 between outlet valve 28 and compressor inlet 23, these reservoirs serving in use as buffers to eliminate fluctuation in pressure of gas admitted to tube 10 through inlet valve 26 or exhausted from tube 10 through outlet valve 28.
  • Tube 10 which is made of stainless steel, is of circular cross section having an internal diameter of and a Wall thickness of A and is about 2'6" long, being closed at its end 11, as previously stated, and open at the other end 33,
  • regenerator 12 comprising a stainless steel cylinder 34 of about 1" diameter and 2" long, packed with 400500 discs 35 of 200 mesh stainless steel gauze. Each disc 35 extends transversely of cylinder 34, and the total weight of the discs is about 45 grams.
  • An apertured cover plate 36 extends across the end of cylinder 34 so as to prevent the discs from moving into the interior of tube While allowing gas to flow thereto.
  • a short length of stainless steel pipe 20 which passes through the wall of insulating box 19 and communicates with gas line 21 between inlet valve 26 and outlet valve 28.
  • Pipe 20 communicates with the interior of cylinder 34 through a cover plate 37 which is apertured similarly to cover :plate 36 so as to prevent the discs from moving into pipe 20 while allowing gas to flow between the pipe and the cylinder.
  • the heat exchange means 13 comprises a length of stainless steel tubing about 10" long which is silver soldered to the tube 10 along the portion thereof which extends inwardly from closed end 11, and is connected by supply and return lines 14 and 15 to a source of cooling water disposed outside cold box 19.
  • heat exchange means 16 comprises a length of stainless steel tubing about 6" long which is silver soldered to tube 10 along the portion thereof which is near open end 33 and is connected to supply and return lines 17 and 18 for circulating a cold-transferring fluid refrigerant therethrough.
  • tubing 13 constitutes a heat-sink while tubing 16 c0nstitutes a cold-sink.
  • a suitable working gas is argon which has a high ratio between its specific heat at constant pressure and specific heat at constant volume, and an example of operation of this apparatus using argon will now be described.
  • the compressor 24 delivers argon at room temperature and a pressure of 220 pounds per square inch gauge to reservoir 31 whence argon is taken at substantially 220 p.s.i.g. according as valves 26 and 28 are opened and closed in a repeated cycle determined by the operation of the solenoids 27 and 29.
  • inlet valve 26 is opened and allowed to remain open for 0.24 second while outlet valve 28 remains closed. Consequently a charge of argon flows through pipe and regenerator 12 into tube 10 until a pressure of substantially 220 p.s.i.g. is attained therein near closed end 11.
  • outlet valve 28 is opened and remains open for 0.24 second, while inlet valve 26 remains closed.
  • Argon thereupon flows from tube 10 through regenerator 12 and pipe 20 to reservoir 32 and thence to the compressor inlet 23 at a pressure of almost 0 p.s.i.g.
  • the compressed argon is expanded and, having lost heat to the cooling water, is thereby cooled to a temperature below room temperature.
  • the wall of tube 10 near open end 33 is therefore cooled, and the regenerator discs 35 are also cooled.
  • inlet valve 26 opens again and the cycle is repeated, a complete cycle therefore taking 0.57 second.
  • Argon entering tube 10 when the cycle is repeated is initially cooled in passing through the regenerator 12 but compression of the gas in tube 10 causes heating .at its end 11. Heat is removed by heat sink 13 before the gas is cooled on expansion giving up cold to the cold sink 16 and being warmed to room temperature on passing through the regenerator 12.
  • the regenerator 12 After approximately minutes of operation, the regenerator 12 has been cooled to a temperature of about K. at the end thereof adjacent tube 10, while at its end communicating with pipe 20 the temperature of the regenerator is about 290 K., .a rectilinear temperature gradient extending through the regenerator.
  • These are equilibrium temperatures at which the regenerator is not further cooled by continued operation of the apparatus, and when equilibrium is reached, continued operation of the apparatus makes cold available to the cold sink.
  • the argon compressed at the end 11 of tube 10 attains a mean temperature of 350 K. after equilibrium is reached, while the wall of the tube near that end is maintained at about 290 K.
  • Some improvement in heat transfer from the tube may be effected by making its warm end of a material more conductive than stainless steel, but stainless steel offers the advantage that there is no excessive conduction along the tube and the heat transfer is adequate.
  • the wall of the tube is maintained at a temperature of 150 K., and refrigeration is delivered at this temperature at the rate of about 1 Watt to a cold-transferring liquid or gas which is continuously circulated between cold sink 34 and the point at which refrigeration is required.
  • the dimensions of the tube may advantageously vary so as to give a cross-sectional area between one sixteenth and one half of a square inch, and a length between eighteen inches and six feet.
  • the cross-sectional area may be up to four square inches.
  • Gases other than argon may be used, and in particular air may be used, being taken from an available source of compressed air and being exhausted from the tube to atmosphere.
  • Gas pressures used preferably lie in the range 150 to 300 p.s.i.g.
  • the valves are suitably timed so that the apparatus operates between 200 cycles and 5 cycles a minute, a preferred rate being between 150 and 60 cycles a minute, the inlet valve preferably being open for the same length of time as the outlet valve while the interval between the closure of one valve and the opening of the other is preferably not more than 0.05 second.
  • Cooling of the warm end to a temperature below room temperature can be achieved by coupling two or more tubes operating in a similar fashion to tube 10 so that the cold end of one cools the warm end of the next succeeding tube.
  • Refrigeration apparatus in which two tubes are coupled in a particularly advantageous way for this purpose is illustrated in FIGURES 3 and 4.
  • Tube 10 is spaced from regenerator cylinder 34 by a distance a little over one foot, and the open end 33 of the tube is connected to cylinder 34 of regenerator 12 by a copper tube 38 of A2" internal di ameter.
  • Copper tube 38 communicates with an annular channel 39 formed in a cover plate 40 of cylinder 34, channel 39 in turn communicating with the interior of the cylinder 34 through holes 41.
  • the central portion 42 of cover plate 40 is formed with holes 4-3 through which gas can pass from regenerator 12 to a further regenerator 44.
  • Regenerator 44 comprises a cylinder 45 of about /2 internal diameter and 1" long, and is made of stainless steel, being packed similarly to cylinder 34 with 200 mesh stainless steel gauze discs 46. Cylinder 45 communicates at its end remote from cylinder 34 with the open end 47 of a stainless steel tube 48 of internal diameter and about 1'6 long which extends parallel to tube 38 and overlaps tube 10. Tube 48 has a closed end 49, and the end portion of tube 48 adjacent end 49 is silver-soldered to the overlapped end portion of tube A cold sink 50 about 4" long and similar to cold sink 16 shown in FIGURE 2 is silver-soldered to tube 48 near its open end 47 and has supply and return pipes 51 and 52.
  • FIGURE 3 The arrangement shown in FIGURE 3 is provided with a compressor 24, valves 26 and 28 and reservoirs 31 and 32 fitted to the pipe line 21 as shown in FIGURE 1.
  • valves 26 and 28 are opened and closed to admit argon at a pressure of 200 p.s.i.g. and exhaust argon to a pressure of 0 p.s.i.g. while the warm end-portion of tube 10 is cooled by cooling water, exactly as described for the preceding example.
  • the portion of tube 10 adjacent open end 3-3 is thereby cooled, thus cooling the warm end portion of tube 48.
  • a first stage of refrigeration occurs
  • tube 48 a second stage of refrigeration occurs.
  • the cold-end portion of tube 48 and the adjacent regenerator packing discs 46 are in consequence cooled to a temperature of about 120 K., and when equilibrium is reached refrigeration is available at this temperature at the rate of 1.5 watts.
  • valve timings and consequent changes of gas pressure within the tubes for the two stage apparatus are illustrated in FIGURES 5a and 50 respectively. It will be apparent that the valve timings are the same as for the single stage operation, the pressure changes for which are shown in FIGURE 5b.
  • More than two tubes can be coupled together to produce still lower temperatures, down to K.
  • FIGURE 6 A suitable arrangement of a three-stage unit is schematically illustrated in FIGURE 6, in which 51 represents the compressor (with in-built after-cooler), 52 and 53 the two reservoirs, 54 and 55 the inlet and outlet valves respectively, 56 the gas pipe line, 57, 5'8 and 5-9 the three elongated tubular members with thermal regenerators 60, 61 and 62 respectively. Heat is abstracted from the closed ends of tubular members 57, 58 and 5-9 by indirect heat exchange at points 63, 64 and 65 respectively and refrigeration is supplied at end 66 of tubular member 59. 6 7 is the thermal insulating or cold box.
  • the fluid circulated through tubing 16 may be any suitable gas or liquid which does not freeze at the low temperatures attained. Nitrogen, hydrogen, argon, helium or air may, for example, be used where appropriate. An organic liquid such as acetone may be used under suitable conditions of temperature.
  • an article to be cooled to, and maintained at, a low temperature may be soldered or clamped to the tube 10 in place of the tubing 16.
  • thermal regenerator any means which is adapted in successive operations to abstract heat from, and to give up heat to, a gas passing therethrough.
  • the heat exchange means which may be used for the circulation of a fiuid in thermal contact with the tubular member 10 may be arranged externally of the tube 10 in physical contact therewith or may be within the tube with connections leading to the outside of the tube.
  • Refrigeration apparatus comprising a tubular memher which is open at one end and closed at the other end, a thermal regenerator in communication with the open end of the tubular member, a gas conduit in communication with the thermal regenerator so that gas under pressure may be passed from the gas conduit through the thermal regenerator to the tubular member and exhausted with expansion from the tubular member through the thermal regenerator to the gas conduit, the thermal regenerator serving to abstract heat from gas entering the tubular member and return heat to gas leaving the tubular member, valve means in said gas conduit for controlling the flow of gas to and from the tubular member and arranged to permit the gas to enter and leave the tubular member as a succession of charges and heat exchange means adjacent the closed end of the tubular member for enabling a coolant to be passed in thermal contact with the tubular member adjacent to the closed end thereof, whereby on operation of the apparatus with gas under pressure being fed into, and exhausted with expansion from, the tubular member as a succession of charges and with a coolant passing through the said heat exchange means refrigeration is made available near the open end of the tub
  • Refrigeration apparatus as claimed in claim 1, in which the tubular member is a tube of internal crosssectional area of from one sixteenth to one half of a square inch, and of a length of from eighteen inches to six feet.
  • Refrigeration apparatus as claimed in claim 2, in which the tubular member is made of stainless steel and has a wall-thickness between 0.02 inch and 0.1 inch.
  • valve means include a single inlet valve and a single outlet valve common to all the tubular members and the passage means is arranged to admit gas in parallel to the tubular members.
  • Multi-stage refrigeration apparatus as claimed in claim 4 including first and second tubular members, and having a first thermal regenerator arranged to cool gas being admitted to the first and second tubular members, and a second thermal regenerator arranged to further cool gas being admitted to the second tubular member.
  • Multi-stage refrigeration apparatus as claimed in claim 5, in which the open end of the first tubular member is spaced from the first thermal regenerator by a relatively narrow tubular gas passage, and the second tubular member extends parallel to and adjacent the tubular gas passage, a portion of the second member near its closed end overlapping a portion of the first member near its open end and adjacent portions of the first and second members being in thermal contact so that the first member provides refrigeration for the second member.
  • a unit for use in refrigeration apparatus comprising a tube open at one end and closed at the other end, heat exchange means secured to the tube in thermal contact therewith adjacent its closed end, a housing with an opening at each end secured to the tube in communication with the open end of the tube and heat-absorbing packing within the housing for abstracting heat from gas entering the tube and for delivering heat to gas leaving the tube.
  • a method of producing refrigeration which comprises repeatedly performing the cycle of admitting compressed gas to a relatively long and narrow chamber through an inlet situated at one end thereof, with abstraction of heat from the gas before it enters the chamber, cooling gas in the chamber by indirect heat exchange near the end thereof remote from the inlet, and exhausting compressed gas from the chamber through the inlet with expansion thereof within the chamber and with return of abstracted heat to the gas after it leaves the chamber, whereby refrigeration is made available at the end of the chamber adjacent the inlet.
  • Refrigeration apparatus comprising 'a tubular member which is open at one end and closed at the other end, a thermal regenerator in communication with the open end of the tubular member, a gas conduit in communication with the thermal regenerator so that gas under pressure may be passed from the gas conduit through the thermal regenerator to the tubular member and exhausted with expansion from the tubular member through the thermal regenerator to the gas conduit, the thermal regenerator serving to abstract heat from gas entering the tubular member and return heat to gas leaving the tubular member, valve means in said gas conduit for controlling the flow of gas to and from the tubular member and arranged to permit the gas to enter and leave the tubular member as a succession of charges, heat exchange means adjacent the closed end of the tubular member for enabling a coolant to be passed in thermal contact with the tubular member adjacent to the closed end thereof whereby on operation of the apparatus with gas under pressure being fed into, and exhausted with expansion from, the tubular member as a succession of charges and with a coolant passing through the said heat exchange means refrigeration is made available near the open end of the tubular member
  • Refrigeration apparatus as claimed in claim 9 in which the thermal regenerator comprises a housing with an opening at each end and packed with discs of metal gauze, each disc extending transversely of the direction of gas flow through the housing.
  • Refrigerator apparatus as claimed in claim 9 in which the said heat exchange means for the passage of coolant includes at least one tube which extends parallel to the tubular member and in thermal contact therewith adjacent the closed end thereof.
  • a method of producing refrigeration which comprises repeatedly performing the cycle of admitting compressed gas to a relatively long and narrow chamber through an inlet situated at one end thereof, with abstraction of heat from the gas before it enters the chamber, cooling gas in the chamber by indirect heat exchange near the end thereof remote from the inlet, and exhausting compressed gas from the chamber through the inlet With expansion thereof Within the chamber and With return of abstracted heat to the gas after it leaves the chamber, said admitting and exhausting of compressed gas being for substantially equal periods of time, whereby refrigeration is made available at the end of the chamber adjacent the inlet.
  • a method 'as claimed in claim 12 in which the gas is admitted to the chamber at a pressure between 150 and 300 pounds per square inch.
  • a method as claimed in claim 12 in which compressed gas is simultaneously admitted to and exhausted from a plurality of chambers, and refrigeration made available at the wall of one chamber is used to cool the Wall of another chamber near the end thereof remote from the inlet so that lower temperature refrigeration is made available at the wall of said another chamber adjacent the inlet thereof.
  • Multi -stage refrigeration apparatus comprising at least two elongated tubular members each open at one end and closed 'at the other end, gas passage means in communication with the open end of each tubular member through a thermal regenerator whereby gas under pressure may be passed from the gas passage means through the thermal regenerator into each tubular member and exhausted with expansion from the tubular member back through the thermal regenerator and through the gas passage means, the thermal regenerator in each case serving to extract heat from the gas entering the tubular member and returning heat to the gas leaving the tubular member, valve means for controlling the admission of gas to, and exhaustion of gas from, the tubular members, the valve means being arranged to permit the gas to enter and leave the tubular members as a succession of charges, and means for the passage of coolant in thermal contact with a first tubular member adjacent the closed end thereof, the part of each succeeding tubular member adjacent its closed end being thermally linked to the part adjacent the open end of the preceding member for indirect heat exchange therewith, whereby a succession of admissions of gas under pressure to the tubular members with

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Separation By Low-Temperature Treatments (AREA)
US357902A 1963-04-10 1964-04-07 Refrigeration apparatus Expired - Lifetime US3302422A (en)

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Application Number Priority Date Filing Date Title
GB14351/63A GB1084736A (en) 1963-04-10 1963-04-10 Improvements in refrigeration apparatus

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US3302422A true US3302422A (en) 1967-02-07

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US357902A Expired - Lifetime US3302422A (en) 1963-04-10 1964-04-07 Refrigeration apparatus

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US (1) US3302422A (fr)
DD (1) DD55680A5 (fr)
FR (1) FR1389960A (fr)
GB (1) GB1084736A (fr)
NL (1) NL6403817A (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3431746A (en) * 1966-02-21 1969-03-11 British Oxygen Co Ltd Pulse tube refrigeration process
US3630041A (en) * 1970-02-25 1971-12-28 Philips Corp Thermodynamic refrigerator
US3817044A (en) * 1973-04-04 1974-06-18 Philips Corp Pulse tube refrigerator
US5269147A (en) * 1991-06-26 1993-12-14 Aisin Seiki Kabushiki Kaisha Pulse tube refrigerating system
US20100313589A1 (en) * 2009-06-13 2010-12-16 Brent Alden Junge Tubular element

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5107683A (en) * 1990-04-09 1992-04-28 Trw Inc. Multistage pulse tube cooler
DE102005035892B4 (de) * 2005-07-30 2012-07-12 Bruker Biospin Gmbh Magnetresonanzapparatur mit Druckreservoir

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1321343A (en) * 1919-11-11 vuilleumier
US1459270A (en) * 1914-05-14 1923-06-19 Safety Car Heating & Lighting Method of and apparatus for heat differentiation
US3237421A (en) * 1965-02-25 1966-03-01 William E Gifford Pulse tube method of refrigeration and apparatus therefor

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1321343A (en) * 1919-11-11 vuilleumier
US1459270A (en) * 1914-05-14 1923-06-19 Safety Car Heating & Lighting Method of and apparatus for heat differentiation
US3237421A (en) * 1965-02-25 1966-03-01 William E Gifford Pulse tube method of refrigeration and apparatus therefor

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3431746A (en) * 1966-02-21 1969-03-11 British Oxygen Co Ltd Pulse tube refrigeration process
US3630041A (en) * 1970-02-25 1971-12-28 Philips Corp Thermodynamic refrigerator
US3817044A (en) * 1973-04-04 1974-06-18 Philips Corp Pulse tube refrigerator
US5269147A (en) * 1991-06-26 1993-12-14 Aisin Seiki Kabushiki Kaisha Pulse tube refrigerating system
US20100313589A1 (en) * 2009-06-13 2010-12-16 Brent Alden Junge Tubular element

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NL6403817A (nl) 1964-10-12
FR1389960A (fr) 1965-02-19
DD55680A5 (de) 1967-05-05
GB1084736A (en) 1967-09-27

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