US3383872A - Device for producing cold with cold loss prevention means - Google Patents

Device for producing cold with cold loss prevention means Download PDF

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Publication number
US3383872A
US3383872A US594745A US59474566A US3383872A US 3383872 A US3383872 A US 3383872A US 594745 A US594745 A US 594745A US 59474566 A US59474566 A US 59474566A US 3383872 A US3383872 A US 3383872A
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Prior art keywords
cold
space
piston
temperature
gap
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US594745A
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English (en)
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Kohler Jacob Willem Laurens
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US Philips Corp
North American Philips Co Inc
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US Philips Corp
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    • 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

Definitions

  • FIG.1 A first figure.
  • the invention relates to a device which comprises at least one cylinder having a piston-like member reciprocating therein, said piston-like member being capable of varying the volume of an expansion space in said cylinder, in which space, during operation, an average temperature prevails which is lower than the ambient temperature.
  • a gap is present between said member and a cylinder Wall cooperating therewith and communicating on one side with said space, the said gap being bounded on its side remote from said space by a seal between the piston-like member and the cylinder wall.
  • Devices of this type are known and may be constructed, for example, as a piston expansion machine in which a high-pressure medium is reduced in pressure at low temperature.
  • Such a refrigerator comprises one or more compression spaces which have a variable volume and one or more expansion spaces communicating therewith which likewise have :a variable volume and in which, during operation, lower average temperatures prevail than in the said compression spaces.
  • a regenerator is arranged in the communication between each pair of the spaces while for varying the volume of said spaces piston-like members are provided which are movable with a mutual phase difference.
  • a double-acting piston-like member reciprocates in a closed cylinder.
  • the space on one side of the piston-like member has a lower average temperature than the space on the other side of said member.
  • These two spaces communicate with one another through a regenerator in which the space which is at a higher temperature can be made to communicate alternately with a high-pressure container and with a low-pressure container.
  • the communication with the low pressure container is effected when the volume of the coldest space is substantially at a maximum so that therein mainly expansion occurs.
  • the piston-like body which can vary the volume of the expansion space in general has thin walls and a rather large height. This is done to insulate the cold expansion space from the space on the other side of the piston-like member. It has the further advantage that the seal between the piston-like member and the cylinder cooperating therewith can be effected at a distance from the cold space and consequently at a higher temperature. At the area of the seal the piston-like member and the cylinder have a difference in diameter which is as small as possible.
  • the invention is based on the recognition of the fact that the flow of cold from the expansion space decreases when the temperature gradient is smaller in the axial direction.
  • the device according to the invention is characterized in that it comprises means for additionally cooling said wall of the piston-like member and/ or the cylinder which bounds the said gap over at least one part of the axial length along the whole circumference.
  • the walls of the piston-like member and of the cylinder which bound the gap have stepped constructions in such manner that, viewed in the axial direction, the gap is divided into at least two parts, one part of the gap being located nearer to the coldest expansion space having a smaller diameter than the part of the gap located farther remote from the said space, so that the volume of the space, influenced by the annular surfaces formed as a result of the stepped construction, can vary in phase with the volume of the coldest expansion space.
  • cold is produced in the said spaces, so that the temperature gradient in the gap and its walls will be smaller than in the known refrigerators.
  • the walls of the gap serve as regenerators for medium flowing into and out of the said spaces. In this manner a local cooling of the walls of the gap is obtained with very simple means.
  • the wall of the piston-like member and the cylinder which bound the gap have conical constructions at least ever part of their axial length, the smallest diameter of said walls being located in the direction of the coldest expansion space.
  • cold will be produced again in the space which is bounded by the conical walls so that said conical walls are cooled. As a result of this, the temperature gradient in the gap will be decreased.
  • one or more places of the wall of the cylinder and/or the piston-like member which also bounds said gap are each in a heatconducting relationship with a source of cold along the whole circumference, each of said sources of cold having a lower temperature than the place communicating therewith so that thermal energy can be withdrawn from these places.
  • FIGURE 1 is a diagrammatic cross-sectional view of a known cold-gas refrigerator.
  • FIGURE 2 is a diagrammatic cross-sectional view of a cold-gas refrigerator in which the walls of the displacer part, which influences the expansion space with the lowest temperature, and the cylinder cooperating therewith have stepped constructions.
  • FIGURE 3 is a diagrammatical cross-sectional view of a cold-gas refrigerator in which the walls of the displacer part, which influences the expansion space with the lowest temperature, and a cylinder cooperating therewith have a conical construction.
  • FIGURE 4 is a diagrammatic view of another coldproducing device in which the piston-like member which can vary the volume of the expansion space as well as the cylinder cooperating therewith have stepped constructions.
  • FIGURE 5 is a diagrammatic cross-sectional View of a cold-producing device comprising two cold-gas refrigerators which supply their cold at different temperatures and in which the cold part of the refrigerator which supplies its cold at the higher temperature is in a heatconducting relationship with a place of the part of the cylinder wall which cooperates with the last displacer stage.
  • FIGURE 1 shows a known cold-gas refrigerator which comprises a compression piston 1 which can vary with its working face the volume of a compression space 2.
  • Reference numeral 3 denotes a displacer which consists of two parts 4 and 5 having different diameters.
  • the worxing face of the displacer part 4 can vary the volume of an expansion space 6 while the annular surface 7 can vary the volume of an intermediate expansion space 8.
  • the compression piston 1 and the displacer 3 are connected by means of a piston rod 9 and a displacer rod 10, respectively, to a gear not shown which can move said members with a mutual phase difference.
  • the compression space 2 communicates, through a cooler 11, a first regenerator 12, and a first freezer 13, with the intermediate expansion space 8.
  • the intermediate expansion space 8 communicates with the expansion space 6 through a second regenerator 14 and a second freezer 15.
  • the displacer part 4 is incorporated with some play in the cylinder part cooperating therewith so that between said displacer part and the cylinder a narrow gap 17 is formed which at its top side is in open communication with the expansion space 6 and is closed at its lower side by the seal 18 arranged on the displacer part 4. Said seal consequently is at a higher temperature than the expansion space 6.
  • the displacer part 5 having the larger diameter is constructed in a corresponding manner.
  • FIGURE 2 shows a cold-gas refrigerator which in outline corresponds to the cold-gas refrigerator shown in FIGURE 1.
  • the displacer part 4 and the cooperating cylinder wall have stepped constructions so that annular surfaces 20 and 21 are formed which can vary the volume of the spaces 22 and 23.
  • These spaces communicate with the expansion space 6 through the parts 17 and 17" of the narrow gap. Since the volume variations of the spaces 22 and 23 are in phase with those of the expansion space 6, said spaces also constitute expansion spaces so that cold will be produced therein, the walls of the parts 17' and 17" of the gap serving as regenerators for the medium which flows into and out of the spaces 22 and 23, respectively.
  • the volume of the space 25 influenced by the conical part of the displacer will vary in phase with the volume of the space 6, so that the space 25 also is an expansion space. So in this space also cold will be produced but not at the low temperature which prevails in the space 6 but at a higher temperature. The loss of cold from the space 6 will consequently be smaller than in the refrigerator shown in FIGURE 1, while the cold leakage from the space 25 has been produced at a higher temperature and consequently with a better efiiciency.
  • FIGURE 4 diagrammatically shows a cold-producing device which comprises a double-acting piston-like member 31 reciprocating in a closed cylinder 30.
  • the two spaces 32 and 33 on either side of the piston-like member 31 communicate with one another.
  • a regenerator 34 is included.
  • the piston-like member 31 is connected to a gear not shown, through a piston rod 35.
  • the duct 36 communicates with the inlet of a compression device 42 through a storage container 40 and a heat exchanger 41.
  • the duct 37 commmunicates with the outlet of the compressor 42 through a buffer container 43 and the heat exchanger 41.
  • This device operates as follows: When the piston 31 is substantially in its lowest position (the volume of the space 33 then is substantially at a maximum) the valve 39 is opened and the whole system is filled with the highpressure medium. In the opened condition of the valve 39 the piston 31 moves upwards. When the piston 31 has reached its uppermost condition (the volume of the space 32 then is at a maximum) the valve 39 is closed and the valve 38 is opened. If desired, the operation in the said manner of the valves is possible during the upward stroke of the piston 31. At the decrease in pressure caused by opening the valve 38, the medium will become colder so that in space 32 a given production of cold is obtained. A very low average temperature, for example, K. will adjust in the space 32.
  • the piston 31 has a stepped construction.
  • the piston 31 comprises annular surfaces 45 and 46 which vary the volume of the spaces 47 and 48 in the same phase as the volume of the space 32. So these spaces also are expansion spaces so that therein cold is also produced but at a higher temperature and consequently with a better efficiency. So in this device loss of cold from the space 32 will be checked in the same manner as in the cold-gas refrigerator shown in FIGURE 2.
  • loss of cold from the coldest expansion stage is checked by producing cold at a higher temperature and cooling the walls of the gap with said cold. This additional cold is produced by the machine itself.
  • FIGURE 5 This is diagrammatically shown in FIGURE 5.
  • This figure shows two cold-gas refrigerators A and B, arranged beside one another.
  • the expansion space 6 of the refrigerator A cold is produced at a temperature of 20 K.
  • the expansion space 6 of the refrigerator B cold is produced at a temperature of, for example, K.
  • the 7 cold expansion space 6 of the refrigerator B communicates, through a system of ducts 50 containing a medium, with a place 51 of the cylinder wall which also bounds the gap 17.
  • the said space 51 is chosen to be so that without additional cooling it would have a temperature exceeding 30 K.
  • the medium in the duct system 50 is chosen to be so that at 20 K. it will condense against the walls of the expansion space 6 of the refrigerator B and evaporate at the place 51, thus cooling the cylinder wall. In this manner the temperature gradient in the refrigerator A between the space 6 and the place 51 is smaller than when no cooling would take place. As a result of this the loss of cold from the space 6 of refrigerator A will be smaller than in the known cold-gas refrigerator shown in FIGURE 1.
  • the duct system 50 may be replaced, if desired, by another heat-conducting connection, for example, a copper tube.
  • a device provided with at least one cylinder, a piston reciprocating in said cylinder and together defining an expansion space, said piston being capable of varying the volume of said expansion space in said cylinder, the average temperature in said space being lower than the ambient temperature, a gap located between said piston and adjacent cylinder wall and communicating with said expansion space, a seal bounding said gap at a location remote from said space and positioned between said piston and adjacent cylinder wall, and means for additionally cooling the wall of said piston and/or cylinder which bounds said gap over at least one part of the axial length along the entire annular area.
  • a device as claimed in claim 1 wherein the walls of said piston and adjacent cylinder bounding said gap are stepped in construction to form a plurality of expansion spaces of varying degrees of cold whereby when viewed in an axial direction said gap is divided into at least two parts, one part being located nearer to the coldest expansion space having a smaller diameter than the part of the gap which is farther remote from said coldest expansion space whereby the volume of the spaces influenced by the annular surfaces formed as a result of the stepped construction can vary in phase with the volume of said coldest expansion space.
  • a device as claimed in claim 4 having two spaced cylinders, each of said cylinders being provided with a piston therein adapted for reciprocation, and a duct system connecting one expansion space in one of said cylinders to said location in the other of said cylinders.
  • a device as claimed in claim 4 having two spaced cylinders, each of said cylinders being provided with a piston therein adapted for reciprocation, and a copper tube connecting one expansion space in one of said cylinders to said location in the other of said cylinders.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
US594745A 1965-12-05 1966-11-16 Device for producing cold with cold loss prevention means Expired - Lifetime US3383872A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
NL6515725A NL6515725A (enrdf_load_stackoverflow) 1965-12-05 1965-12-05

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US3383872A true US3383872A (en) 1968-05-21

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US (1) US3383872A (enrdf_load_stackoverflow)
BE (1) BE690543A (enrdf_load_stackoverflow)
DE (1) DE1501107A1 (enrdf_load_stackoverflow)
FR (1) FR1504138A (enrdf_load_stackoverflow)
GB (1) GB1168818A (enrdf_load_stackoverflow)
NL (1) NL6515725A (enrdf_load_stackoverflow)
SE (1) SE321249B (enrdf_load_stackoverflow)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4277947A (en) * 1980-04-16 1981-07-14 The United States Of America As Represented By The Secretary Of The Army Cryogenic cooler having telescoping multistage regenerator-displacers
US4522032A (en) * 1982-09-24 1985-06-11 Aisin Seiki Kabushiki Kaisha Stirling-cycle refrigerator

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4143520A (en) * 1977-12-23 1979-03-13 The United States Of America As Represented By The Secretary Of The Navy Cryogenic refrigeration system

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2857220A (en) * 1954-01-22 1958-10-21 Philips Corp Hot-gas reciprocating engine
US2907175A (en) * 1954-03-19 1959-10-06 Philips Corp Cold-gas refrigerating apparatus
US3145629A (en) * 1960-12-13 1964-08-25 Union Carbide Corp Cryogenic pump sealing rings
US3214924A (en) * 1962-07-26 1965-11-02 Philips Corp Method of absorbing thermal energy at low temperatures and apparatus for carrying out such methods
US3218815A (en) * 1964-06-17 1965-11-23 Little Inc A Cryogenic refrigeration apparatus operating on an expansible fluid and embodying a regenerator
US3292501A (en) * 1963-12-24 1966-12-20 Philips Corp Device including at least one cylinder with a piston-shaped body which is movable therein

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2857220A (en) * 1954-01-22 1958-10-21 Philips Corp Hot-gas reciprocating engine
US2907175A (en) * 1954-03-19 1959-10-06 Philips Corp Cold-gas refrigerating apparatus
US3145629A (en) * 1960-12-13 1964-08-25 Union Carbide Corp Cryogenic pump sealing rings
US3214924A (en) * 1962-07-26 1965-11-02 Philips Corp Method of absorbing thermal energy at low temperatures and apparatus for carrying out such methods
US3292501A (en) * 1963-12-24 1966-12-20 Philips Corp Device including at least one cylinder with a piston-shaped body which is movable therein
US3218815A (en) * 1964-06-17 1965-11-23 Little Inc A Cryogenic refrigeration apparatus operating on an expansible fluid and embodying a regenerator

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4277947A (en) * 1980-04-16 1981-07-14 The United States Of America As Represented By The Secretary Of The Army Cryogenic cooler having telescoping multistage regenerator-displacers
US4522032A (en) * 1982-09-24 1985-06-11 Aisin Seiki Kabushiki Kaisha Stirling-cycle refrigerator

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Publication number Publication date
BE690543A (enrdf_load_stackoverflow) 1967-06-01
GB1168818A (en) 1969-10-29
DE1501107A1 (de) 1969-10-23
NL6515725A (enrdf_load_stackoverflow) 1967-06-05
FR1504138A (fr) 1967-12-01
SE321249B (enrdf_load_stackoverflow) 1970-03-02

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