EP0454491A2 - Appareil de congélation pour laboratoire - Google Patents

Appareil de congélation pour laboratoire Download PDF

Info

Publication number
EP0454491A2
EP0454491A2 EP91303808A EP91303808A EP0454491A2 EP 0454491 A2 EP0454491 A2 EP 0454491A2 EP 91303808 A EP91303808 A EP 91303808A EP 91303808 A EP91303808 A EP 91303808A EP 0454491 A2 EP0454491 A2 EP 0454491A2
Authority
EP
European Patent Office
Prior art keywords
chamber
heat transfer
freezer
argon
tubes
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP91303808A
Other languages
German (de)
English (en)
Other versions
EP0454491A3 (en
Inventor
C. Tipton Russel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Forma Scientific Inc
Original Assignee
Forma Scientific Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Forma Scientific Inc filed Critical Forma Scientific Inc
Publication of EP0454491A2 publication Critical patent/EP0454491A2/fr
Publication of EP0454491A3 publication Critical patent/EP0454491A3/en
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/0266—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with separate evaporating and condensing chambers connected by at least one conduit; Loop-type heat pipes; with multiple or common evaporating or condensing chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/0435—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines the engine being of the free piston type
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/04—Self-contained movable devices, e.g. domestic refrigerators specially adapted for storing deep-frozen articles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/08—Thermoplastics
    • 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
    • F25B23/00—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect
    • F25B23/006—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect boiling cooling systems
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D23/00—General constructional features
    • F25D23/003—General constructional features for cooling refrigerating machinery
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2400/00—General features of, or devices for refrigerators, cold rooms, ice-boxes, or for cooling or freezing apparatus not covered by any other subclass
    • F25D2400/10—Refrigerator top-coolers

Definitions

  • This invention relates to a cryogenic temperature storage chamber and, more particularly, to a laboratory freezer appliance that provides a freezer storage space, e.g., in the order of 5 to 20 cubic feet (0.14 to 0.57 cubic metres) capable of storage temperatures of -160°C and lower.
  • a laboratory freezer appliance in accordance with one embodiment of the invention comprises an insulated freezer chamber, heat transfer tubes in heat transfer communication with the freezer chamber, the tubes sloping from one end to the other permitting downward flow by gravity of a heat transfer fluid as a liquid along the freezer chamber and the counterflow of the fluid as a vapour, a Stirling cycle heat pump, having a warm zone and a cold zone, a condensing chamber in heat transfer communication with the cold zone for condensing the heat transfer fluid from a vapour to a liquid, and heat transfer fluid distribution means which receives condensed heat transfer fluid from the condensing chamber and distributes it to the heat transfer tubes, and receives vapour from the heat transfer tubes and distributes it to the condensing chamber in a closed cycle of alternate condensation and vaporisation of the heat transfer fluid and consequently cools the freezer chamber.
  • a laboratory freezer appliance in accordance with an embodiment of the invention is characterised in that the heat transfer fluid distribution means does not incorporate physical pumping means.
  • a heat transfer fluid such as argon enters a condensing chamber surrounding the cold end of a Stirling cycle heat pump in the form of argon gas.
  • the argon gas is condensed therein to a liquid at an ultra-low temperature and flows by gravity to an argon distributor having a centrally located liquid argon reservoir and a number of tubes extending around the periphery of the reservoir which substantially evenly deliver the liquid argon refrigerant to heat transfer tubes which extend along either side of the freezer storage chamber in heat transfer communication therewith.
  • the heat transfer tubes slope downwardly from the argon distributor such that the liquid argon flows along the tubes by gravity.
  • the heat transfer tubes are externally finned to provide a large heat transfer surface.
  • the liquid argon in the heat transfer tubes absorbs heat from the interior of the freezer storage chamber causing convective flow of ultra-low temperature air through the storage chamber in turn lowering of the chamber temperature to the desired operating temperature which may be in the order of -160°C or below.
  • the liquid argon is vaporised by the absorbed heat, and the vapour returns to a head space above the reservoir of the argon distributor in the same heat transfer tubes that carry the liquid argon from the distributor.
  • the argon gas then flows from the argon distributor to the condensing chamber surrounding the cold end of the Stirling cycle heat pump where the argon is again condensed to a liquid and returned to the argon distributor in a continuously operating closed cycle refrigeration process.
  • the operating pressure of the system is on the order of 5 bar (500 Kpa). No external pumping means is provided to move the refrigerant through the system thereby eliminating any moving parts and the need for any lubricants which would freeze up at the ultra-low temperatures involved in the cryogenic freezer.
  • the argon gas refrigerant to be cooled circulates in the condensing chamber which is in the form of a pressure vessel external of but surrounding a cold end cup of the Stirling cycle heat pump.
  • the cold end cup is formed of a highly heat conductive material that does not become brittle at temperatures of -160°C or lower, such as a stainless steel, and the outer surface of the cold end cup is provided with a heat conductive sleeve having a series of fins having an Adamak fin profile to increase heat transfer to the argon gas in the condensing chamber.
  • a temperature differential of about 13°C is maintained between the desired storage chamber temperature and the helium in the cold end of the heat pump and about 10°C between the storage chamber temperature and the temperature of the liquid argon.
  • the liquid argon is at -170°C and the helium is at -173°C.
  • the 200 watts of heat input into the helium in condensing the argon gas in the pressure vessel surrounding the cold end cup plus the input work to drive the heat pump compression and expansion cycles are rejected to the environment external of the heat pump by a heat rejector/condenser assembly.
  • Embodiments of this invention provide a laboratory freezer appliance capable of providing consistent and repeatable storage conditions at temperatures of -160°C and lower for extended and unattended storage periods.
  • the freezer has a usable storage space of, e.g., 5 to 20 cubic feet (0.14 to 0.57 cubic metres).
  • the freezer operates on normally available 220 volt AC 50/60 Hz single phase electricity; the installation and start up consists of little more than unpacking and levelling the unit, plugging it into the power source, turning the unit on and waiting for it to cool down from room temperature to operating temperature, e.g., -160°C, which takes only about one-half day; the unit will operate continuously with only occasional unskilled maintenance for the first five years of continuous operation; the unit is configured to use space efficiently; and the aesthetic appearance of the freezer is pleasing and the noise and vibration levels are relatively low. Thus, the unit looks and sounds substantially like a typical household freezer.
  • the cryogenic freezer provides a suitable storage space, e.g., from 5 to 20 cubic feet (0.14 to 0.57 cubic metres), capable of providing a consistent and uniform freezer temperature of -160°C or lower.
  • a suitable storage space e.g., from 5 to 20 cubic feet (0.14 to 0.57 cubic metres)
  • there is no traditional petroleum-based lubrication in the system which otherwise would be subject to freezing by virtue of the ultra-low temperatures of the system and to contamination of the refrigerant and the working gas in the heat pump. Rather, the moving parts of the heat pump are spun during operation to provide hydrodynamic non-contact gas bearings which, since no contact between rotating and stationary parts is allowed, eliminates the need for traditional lubricants.
  • Fig. 1 is an isometric view of an embodiment of a cryogenic freezer according to the present invention.
  • Fig. 2 is a front view of the embodiment of Fig. 1 with walls broken away to show internal components.
  • Fig. 3 is a view along line 3-3 of Fig. 2.
  • Fig. 4 is a view along line 4-4 of Fig. 2.
  • Fig. 5 is a view along line 5-5 of Fig. 4.
  • Fig. 6 is a view along line 6-6- of Fig. 5.
  • Fig. 7 is a cross-sectional view of the cold end heat exchanger, displacer, and rejector assembly of the Stirling cycle heat pump.
  • the cryogenic freezer 10 includes a cabinet 11 which houses a freezer storage chamber 12 interiorly of the cabinet 11, a lid 14 to seal closed the freezer storage chamber 12 and to provide access thereto, and a side car cabinet 16.
  • An access panel 18 provides access to the Stirling cycle heat pump 20 (Fig. 2), which will be described in detail below.
  • a condenser 22 and blower 24 are housed in the side car cabinet 16. The blower 24 draws air through a grill 26 (Fig. 1) in an end wall 27 of the cabinet 16 and over the condenser 22 to condense a refrigerant for removing heat from the heat pump 20, as also will be described in detail below.
  • the freezer 10 is generally rectangular in shape making it suitable for efficient use in a laboratory.
  • the cabinet 11, lid 14, and side car 16 are formed of cold-rolled steel which is painted for protection and aesthetics.
  • Typical physical dimensions of the freezer 10 are an overall external dimension of 91 ⁇ (231cm) long by 46.5 ⁇ (118cm) high by 28.5 ⁇ (72cm) front to back.
  • Typical interior chamber dimensions are 43.5 ⁇ (110cm) long by 32 ⁇ (81cm) high by 16 1/4 ⁇ (41cm) deep, which provides two 42.5 ⁇ (108cm) long by 27 ⁇ (69cm) high by 6 1/4 ⁇ (16cm) deep usable storage volumes, or about 8 cubic feet (0.22 cubic metres) of usable storage volume.
  • Caster wheels 28 are provided to permit convenient movement of the freezer 10 in the laboratory or other facility.
  • the freezer storage chamber 12 is formed of stainless steel for good thermal conductivity and corrosion protection.
  • the storage chamber 12 is surrounded by an insulative material 30 such as a foamed-in-place urethane.
  • the insulation 30 surrounds the bottom, side, and end walls of storage chamber 12 and extends around the Stirling cycle heat pump 20 to isolate the freezer storage chamber 12 and the cold end (shown generally at 32) of the heat pump 20 from the warm heat rejector 34 and compressor assembly 36 of the heat pump 20.
  • a hard, low thermal conductivity plastic panel 38 extends around the top between the freezer chamber 12 and the outer wall of the cabinet 11 and is adhesively joined to the steel cabinet and freezer chamber walls.
  • the freezer lid 14 likewise has a foamed-in-place urethane insulative core 40, and a plastic mat lid liner 42 joined to the lid 14.
  • a snap-in plastic extrusion (not shown) joins the lid 14 and lid liner 42 for foaming of the insulative core 40 in place. This extrusion also retains a bulb gasket 43 in the lid 14 surrounding chamber 12.
  • These fibreglass mat reinforced panels 38, 42 have decreased thermal expansion while maintaining flexibility.
  • a plastic foam sublid 44 rests above the top of the freezer chamber 12.
  • the lid liner 42 is formed to receive a second gasket 46, which may conveniently be a combination of several feather gaskets, adhered in a groove in the plastic lid liner 42.
  • a stainless steel rack 48 is supported interiorly of the freezer storage chamber 12 which in turn supports standard storage boxes or items 50 contained in the freezer chamber 12.
  • the rack 48 is spaced inwardly from the side and bottom walls of the chamber 12 and below the sublid 44, and the storage boxes 50 are in rows spaced from each other down the centre of the chamber 12 (figs. 3 and 4). This results in an open space 52 at the bottom of the chamber 12, spaces 54, 56 along the sides, a space 57 between the rows of storage boxes 50, and a space 58 above the storage boxes 50 and below the sublid 44. These spaces are important to permit circulation by convection of ultra-low temperature air in the freezer storage chamber 12, as described below.
  • a series of heat transfer tubes 60 extend along the length of the storage chamber 12 in the spaces 54, 56 between the inner wall of the chamber 12 and the support racks 48.
  • the tubes 60 are formed of copper for its heat transfer properties and its corrosion resistance.
  • Six vertically spaced tubes 60 are provided along the front of the chamber 12 and six along the rear of the chamber 12 for a total of twelve heat transfer tubes.
  • the tubes 60 include external flat copper fins 62,0.008 ⁇ (0.2mm) thick to increase the heat transfer to the surrounding air.
  • the copper heat transfer tubes 60 circulate a heat transfer fluid along the length of the storage chamber.
  • the preferred heat transfer fluid is argon as a saturated liquid at -170°C when a storage chamber temperature of -160°C is desired.
  • Other heat transfer fluids such as oxygen, nitrogen, and natural gas could be used.
  • Oxygen and natural gas however, have the disadvantage of being flammable, and nitrogen has a higher saturation pressure.
  • Argon on the other hand, is non-flammable and non-explosive at room temperature and atmospheric pressure, and argon has a saturation pressure of less than 50 psig (4.5 Pa) at -170°C.
  • the liquid argon at ultra-low temperatures flows down the heat transfer tubes 60 along the length of the storage chamber 12 by force of gravity due to the tubes 60 being sloped downwardly from their inlet end 64 to their opposite end 66.
  • Gravity flow of the argon refrigerant eliminates the need for a pump which would have moving parts which would require lubrication.
  • the liquid argon in the heat transfer tubes 60 absorbs heat from the storage chamber 12 cooling the surrounding air and causing the argon to vaporise in the tubes 60.
  • the argon gas in the tubes 60 forms a gas head above the liquid in the heat transfer tubes 60 and is transported back to the inlet end 64 of the tubes 60 in a counter-flowing direction to the flow of the liquid argon.
  • An argon distributor 70 whose location is shown generally in Figs. 2 and 4 and whose details are shown in Figs. 5 and 6, is located at the top of the freezer 10 outside of the storage chamber 12 between the cold end 32 of the heat pump 20 and the inlet end 64 of the heat transfer tubes 60.
  • the argon distributor 70 consists of a domed chamber 72 formed of stainless steel, which is welded at its base to a reservoir 74, also formed of stainless steel, having a circular basin 76 therein which is fed with liquid argon through a tube 78 communicating at its other end with the cold end 32 of the Stirling cycle heat pump 20. Twelve liquid argon distribution tubes 80 communicate with the liquid argon reservoir 74 about its circumference.
  • liquid argon distribution tubes 80 open into the bottom of the basin 76 and are spaced about its circumference to achieve a substantially uniform distribution of the liquid argon which flows into and fills the basin 76 to each of the tubes 80.
  • the distribution tubes 80 are joined at their opposite ends to the inlets ends 64 of the twelve heat transfer tubes 60.
  • Argon gas is returned to the argon distributor 70 by flowing through the heat transfer tubes 60, the argon distribution tubes 80, and into a gas head space 84 above the liquid reservoir 74.
  • a second tube 86 e.g., 1 ⁇ (2.54cm) in diameter, connects the head space 84 to a condensing chamber 90 (Fig. 7) at the cold end 32 of the Stirling cycle heat pump 20 where the argon gas is condensed to a liquid, and flows back through feed tube 78 to the reservoir 74 of the argon distributor 70, whereby a continuous cycle of argon condensation, distribution, vaporisation, and condensation occurs.
  • the argon gas from the head space 84 in the argon distributor 70 flows through tube 86 to the condensing chamber 90 at the cold end 32 of the heat pump 20 where it is condensed to a liquid at -170°C or lower.
  • the liquid argon flows back through tube 78, which is slanted downwardly from the condenser 90 toward the distributor 70, into the reservoir 74 of the distributor 70, into the argon basin 76, and then out through the distribution tubes 80 by the force of gravity and into and along the heat transfer tubes 60 along the length of the freezer storage chamber 12.
  • the liquid argon in the tubes 60 absorbs heat in the storage chamber 12 causing the liquid argon to vaporise with the argon gas then returning to the head space 84 in the argon distributor 70 above the liquid reservoir 74 in a counter-flowing relation to the liquid argon and in a continuous sequence of argon gas condensation and vaporisation.
  • the source of refrigeration is the closed cycle, hermertically sealed, free-piston Stirling cycle heat pump 20, which is shown in detail in Fig. 7.
  • the heat pump 20 is vertically disposed and includes the cold end 32 and associated condensing chamber 90 at the top, a heat rejector subassembly 34 therebelow, and the compressor assembly 36 below it.
  • the cold end 32 of the heat pump 20 includes a cold end cup 96 made of stainless steel.
  • the cold end cup 96 is surrounded by a similar stainless steel cap 98 to form the argon condensing chamber 90 therebetween.
  • the cold end cup 96 and condenser chamber cap 98 are joined to an annular stainless steel flange 100 with the cold end cup 96 being welded to the cold end flange 100 at 101 and the chamber cap 98 being welded at annular groove 102 to the flange 100. (The flange is shown diagrammatically in Fig. 7).
  • the liquid argon feed tube 78 and argon vapour tube 86 are welded to the wall of the chamber cap 98 and communicate with openings 103 and 104, respectively, in the wall of the cap 98 permitting flow of argon vapour through opening 104 into the space 105 between the cup 96 and cap 98 where the vapour is condensed to a liquid which then flows out by gravity through opening 103 and into the liquid argon supply tube 78 for return to the distributor 70.
  • the heat rejector assembly 34 includes an outer cylinder 108 mounted at its base 110 in the main support plate 94 and at its top in a groove 112 in the cold end flange 100, and an inner cylinder 114 mounted at its base 116 to the support plate 94. (Again flange 100 is shown diagrammatically).
  • the outer 108 and inner 114 cylinders are formed of seamless stainless steel pipe.
  • the heat rejector assembly 34 further includes a stainless steel upper flange 118 which is joined to the insulation support plate or pan 119 (Fig. 2).
  • the tubes 120 are mounted at their bases in openings 124 in the support plate 94 and at their tops in openings 126 in an upper rejector tube support sheet 128 also formed of stainless steel.
  • the tubes 120 are brazed in place as is tube support sheet 128.
  • the tubes 120 are circumferentially spaced about the unit in three concentric rings.
  • Upper and lower rejector assembly stubs 130 and 132 extend through and are welded in the wall of the outer cylinder 108 of the rejector assembly 34 and communicate with the space 122 surrounding the rejector tubes 120. As will be described below, a refrigerant is circulated in the space 122 to remove heat from the gas passing through the tubes 120.
  • the tubes 120 open at their top ends into a regenerator 134 located between the rejector assembly 34 and the cold end cap flange 100.
  • the regenerator 134 is of standard construction and is a matrix formed of 22 micron diameter stainless steel wire having 80% porosity. Filters 136 are located at the top and bottom of the regenerator 134 to prevent particles of the stainless steel wire from becoming dislodged and being caught in the gas flowing through the regenerator.
  • a displacer support plate 138 which includes a central hub 140 having an internally threaded recess 142 is bolted to the assembly by means of bolts 144 passing upwardly therethrough.
  • a gasket 146 seals the periphery between the displacer support plate 138 and main support plate 94.
  • Set screws 148 are provided in the displacer support plate 138.
  • a displacer support rod 152 is screwed into the recess 142 and then welded to the central hub 140.
  • a displacer assembly 154 includes a cylindrical displacer tube 156, a cylindrical displacer sleeve 157, a shell cap 158, a displacer rod guide 160, which surrounds the displacer rod 152 and to which the displacer sleeve 157 is threaded at its base, a support ring 162, and an insulator 164.
  • the displacer assembly 154 is surrounded by a cold end heat exchanger 168 formed of a phenolic which is threaded to an aluminum cylindrical stuffer 169.
  • the cold end heat exchanger 168 at its end surrounded by the cold end cup 96 contains 30 passages 198 on its outer surface through which the helium gas passes into a gas expansion space 170. Since the gas in space 170 is at a temperature on the order of -173°C, the displacer assembly 154 is made of low thermal conductivity material, such as phenolic, to minimise thermal conduction losses.
  • the end of the stuffer 169 opposite the cold end heat exchanger 168 receives the three bolts 144 securing the displacer support plate 138 in place.
  • a gas spring cap 176 formed of aluminum is threaded to the top of the displacer rod guide 160 forming a generally closed space 178 therein extending down through the centre of the displacer support rod 152, which is filled with helium at an average pressure between the maximum and minimum pressure of the working gas in the heat pump to form a gas spring for the displacer assembly 154.
  • the displacer assembly 154 is spun about its longitudinal axis to provide non-contact hydrodynamic gas bearings between support rod 152 and rod guide 160.
  • heat is rejected from the rejector assembly 34 by the circulation of a refrigerant such as chlorodifluoromethane in the space 122 surrounding the rejector tubes 120. That is, the liquid refrigerant enters the space 122 through the pair of opposed lower stubs 132 (only one shown in Figs. 2 and 7) and absorbs heat from the helium gas passing through the rejector tubes 120 by heat conduction through the tube walls. The absorption of heat from the gas causes the refrigerant to vaporise, and the vapour leaves the rejector through the four circumferentially spaced upper stubs 120 (only one shown in Figs. 2 and 7).
  • a refrigerant such as chlorodifluoromethane
  • Stubs 130 connect with tubing 204 through which the vapour flows to the reflux condenser 22 mounted at the end wall 27 of the side car cabinet 16.
  • the blower 24 is located in the bottom of the side car cabinet 16 and draws air through the grill 26 though a standard air filter 207 and over the condenser tubes 206 to condense the refrigerant therein.
  • the liquid refrigerant then flows by gravity from the condenser 22 through tubing 208 connected to stubs 132 into the bottom of the heat rejector space 122.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP19910303808 1990-04-26 1991-04-26 Laboratory freezer applicance Withdrawn EP0454491A3 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US51476890A 1990-04-26 1990-04-26
US514768 1990-04-26

Publications (2)

Publication Number Publication Date
EP0454491A2 true EP0454491A2 (fr) 1991-10-30
EP0454491A3 EP0454491A3 (en) 1992-03-11

Family

ID=24048612

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19910303808 Withdrawn EP0454491A3 (en) 1990-04-26 1991-04-26 Laboratory freezer applicance

Country Status (1)

Country Link
EP (1) EP0454491A3 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1016701A2 (fr) * 1998-12-28 2000-07-05 Kabushiki Kaisha Toshiba Matériau à accumulation de froid et réfrigérateur à accumulation du froid l'utilisant
EP1167900A1 (fr) * 2000-06-28 2002-01-02 Twinbird Corporation Transfert de chaleur par thermosiphon pour machine frigorifique
EP1255087A1 (fr) * 1998-11-02 2002-11-06 SANYO ELECTRIC Co., Ltd. Dispositif Stirling
EP1312875A1 (fr) * 2000-08-25 2003-05-21 Sharp Kabushiki Kaisha Refroidisseur a cycle de stirling, chambre de refroidissement et refrigerateur
WO2004029526A1 (fr) * 2002-09-24 2004-04-08 The Coleman Company, Inc. Contenant portatif isole a refrigeration
US6758056B1 (en) * 1999-05-12 2004-07-06 Nestec S.A. Apparatus and process for molding frozen ice confectionery compositions into articles

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB349798A (en) * 1929-06-19 1931-06-04 Electrolux Ltd Improvements in heat transferring devices for use in conjunction with refrigerators
US2446686A (en) * 1945-02-26 1948-08-10 Louis H Behrens Refrigerator cabinet and means for maintaining a layer of cold air therein
US2512545A (en) * 1948-06-11 1950-06-20 Frederick E Hazard Structure for and method of transfer, exchange, control regulation, and storage of heat and cold
US3468300A (en) * 1968-11-13 1969-09-23 Acf Ind Inc Heat transfer means for a railway tank car
US3473341A (en) * 1967-01-11 1969-10-21 Philips Corp Cold-gas refrigeration apparatus
US3719051A (en) * 1971-10-26 1973-03-06 Romayne Corp Transportable refrigeration system
US4285394A (en) * 1977-12-12 1981-08-25 Stewart James M Manifold heat exchanger
JPS59165951A (ja) * 1983-03-08 1984-09-19 Aisin Seiki Co Ltd リニアモ−タ−カ−のためのスタ−リングサイクル冷凍機用の冷却装置
EP0245848A1 (fr) * 1986-05-13 1987-11-19 Babcock-Hitachi Kabushiki Kaisha Dispositif d'échangeur de chaleur
US4843826A (en) * 1987-10-09 1989-07-04 Cryodynamics, Inc. Vehicle air conditioner

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB349798A (en) * 1929-06-19 1931-06-04 Electrolux Ltd Improvements in heat transferring devices for use in conjunction with refrigerators
US2446686A (en) * 1945-02-26 1948-08-10 Louis H Behrens Refrigerator cabinet and means for maintaining a layer of cold air therein
US2512545A (en) * 1948-06-11 1950-06-20 Frederick E Hazard Structure for and method of transfer, exchange, control regulation, and storage of heat and cold
US3473341A (en) * 1967-01-11 1969-10-21 Philips Corp Cold-gas refrigeration apparatus
US3468300A (en) * 1968-11-13 1969-09-23 Acf Ind Inc Heat transfer means for a railway tank car
US3719051A (en) * 1971-10-26 1973-03-06 Romayne Corp Transportable refrigeration system
US4285394A (en) * 1977-12-12 1981-08-25 Stewart James M Manifold heat exchanger
JPS59165951A (ja) * 1983-03-08 1984-09-19 Aisin Seiki Co Ltd リニアモ−タ−カ−のためのスタ−リングサイクル冷凍機用の冷却装置
EP0245848A1 (fr) * 1986-05-13 1987-11-19 Babcock-Hitachi Kabushiki Kaisha Dispositif d'échangeur de chaleur
US4843826A (en) * 1987-10-09 1989-07-04 Cryodynamics, Inc. Vehicle air conditioner

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 9, no. 19 (E-292)(1742) 25 January 1985 & JP-A-59 165 951 ( AISHIN SEIKI ) 19 September 1984 *

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1255087A1 (fr) * 1998-11-02 2002-11-06 SANYO ELECTRIC Co., Ltd. Dispositif Stirling
EP1016701A2 (fr) * 1998-12-28 2000-07-05 Kabushiki Kaisha Toshiba Matériau à accumulation de froid et réfrigérateur à accumulation du froid l'utilisant
EP1016701A3 (fr) * 1998-12-28 2001-04-25 Kabushiki Kaisha Toshiba Matériau à accumulation de froid et réfrigérateur à accumulation du froid l'utilisant
US6363727B1 (en) 1998-12-28 2002-04-02 Kabushiki Kaisha Toshiba Cold accumulating material and cold accumulation refrigerator using the same
US6758056B1 (en) * 1999-05-12 2004-07-06 Nestec S.A. Apparatus and process for molding frozen ice confectionery compositions into articles
EP1167900A1 (fr) * 2000-06-28 2002-01-02 Twinbird Corporation Transfert de chaleur par thermosiphon pour machine frigorifique
US6442959B1 (en) 2000-06-28 2002-09-03 Twinbird Corporation Thermosiphon for refrigerating machine
EP1312875A1 (fr) * 2000-08-25 2003-05-21 Sharp Kabushiki Kaisha Refroidisseur a cycle de stirling, chambre de refroidissement et refrigerateur
EP1312875A4 (fr) * 2000-08-25 2004-05-26 Sharp Kk Refroidisseur a cycle de stirling, chambre de refroidissement et refrigerateur
WO2004029526A1 (fr) * 2002-09-24 2004-04-08 The Coleman Company, Inc. Contenant portatif isole a refrigeration
US6751963B2 (en) 2002-09-24 2004-06-22 The Coleman Company, Inc. Portable insulated container with refrigeration

Also Published As

Publication number Publication date
EP0454491A3 (en) 1992-03-11

Similar Documents

Publication Publication Date Title
US5142872A (en) Laboratory freezer appliance
US6550255B2 (en) Stirling refrigeration system with a thermosiphon heat exchanger
RU2162576C2 (ru) Устройство холодильного агрегата бытового компрессионного холодильника
US6266963B1 (en) Apparatus using stirling cooler system and methods of use
CN1246654C (zh) 带有滑出式斯特林制冷组件的售卖机
GB2222872A (en) Apparatus for storing blood
CN108592481A (zh) 采用脉管型自由活塞斯特林制冷机的多温区冰箱
EP0454491A2 (fr) Appareil de congélation pour laboratoire
WO1999058906A1 (fr) Refrigerateur a usage domestique a effet peltier, accumulateurs thermiques et thermosiphons evaporateurs
EP3237820B1 (fr) Système d'étagère réfrigéré
TW514716B (en) Stirling cooling apparatus, cooler, and refrigerator
RU2680453C2 (ru) Теплоизолированный сосуд
CN1586376A (zh) 饮水机制冷装置
KR102040992B1 (ko) 최대 속도로 제품을 냉각 또는 냉동하기 위한 산업에 사용될 수 있는 전기기기
CN211261413U (zh) 一种易于均匀受冷的超低温制冷机
CN111059832B (zh) 冷藏冷冻装置
CN2740102Y (zh) 饮水机制冷装置
RU188391U1 (ru) Холодильник
CN209689257U (zh) 一种超低温冷藏设备
JP2017201222A (ja) 液体冷凍機
KR20070049297A (ko) 김치냉장고
CN111059834B (zh) 冷藏冷冻装置
CN111059844B (zh) 冷藏冷冻装置
US1910853A (en) Absorption refrigerating apparatus
JPH11223404A (ja) スターリング冷却装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH DE DK ES FR GB GR IT LI LU NL SE

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH DE DK ES FR GB GR IT LI LU NL SE

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19920912