Piston/displacer support means for a cryogenic refrigerator

Abstract: A cryogenic refrigerator (10) comprises a compressor (12) including a compressor housing (18) within which a cylinder (20) is mounted, and a piston (22) reciprocable within the cylinder, and a cold finger (14) including a low temperature cylinder (55) within which a displacer (57) is reciprocable, and a regenerator (63) mounted within the displacer. A plurality of flat piston suspension springs (24) include a plurality of spiral slits (24a) to provide a plurality of spiral arms (24b) deflectable as the piston (22) is reciprocated within the compressor cylinder (20). A plurality of annular inner retainers (32) are secured to the piston (22) and adapted to sandwich the inner peripheral edges of the piston suspension springs (24). A plurality of annular outer retainers (30) are secured to the compressor housing (18) and include a plurality of projections (30a) extending inwardly from the outer ends of the spiral slits (24a) to sandwich the outer peripheral edges of the flat piston suspension springs (24).

Description: The present invention generally relates to a cryogenic refrigerator and more particularly, to means for supporting piston/displacer for use in such a cryogenic refrigerator. A conventional stirling refrigerator (see Dr. R.G. Ross, Jr., Tiger/JTJR Briefing, "Oxford Stirling Cooler Technical Overview", October 10, 1989, Jet Propulsion Laboratory California Institute of Technology, Pasadena. CA 91109, or US-A-4 397 155) is designed, for example, to cool infrared sensors to as low as 77K and generally comprises a compressor, and a cold finger connected to the compressor through a conduit. The compressor includes a vertical cylinder fit within the upper end of a compressor housing, and a piston mounted for reciprocal motion within the cylinder. A plurality of flat piston suspension springs are horizontally disposed within the compressor housing to support the piston so as to prevent rubbing contact of the piston with the inner wall of the cylinder and thus, wear of the piston and the cylinder. Each of the piston suspension springs is in the form of a circular disk and includes a plurality of spiral slits to provide a plurality of spiral arms (see Fig. 16). The spiral arms are vertically deflected as the piston is reciprocated within the cylinder. A plurality of annular outer retainers are secured to the inner wall of the housing and arranged to sandwich the outer peripheral edges of the piston suspension springs. Similarly, a plurality of annular inner retainers are secured to a piston rod and arranged to sandwich the inner peripheral edges of the piston suspension springs. In this arrangement, however, the spiral arms are susceptible to fatigue failure as a result of periodic application of local stresses during the normal operation of the compressor. This is due to the fact that the inner and outer ends of the spiral arms are held substantially in point contact with the circumferential edges of the inner and outer retainers (see Fig. 17) and subject to high stress concentration as the spiral arms are deflected. The cold finger includes a low temperature cylinder within which a displacer is reciprocally moved. The displacer has a body and a rod extending downwardly from the body. The interior of the low temperature cylinder is divided by the displacer into two chambers, namely, a low temperature chamber above the displacer, and a high temperature chamber below the displacer body. A regenerator is mounted within the displacer body. A gas port is formed in the displacer body to provide a fluid communication between the low temperature chamber and the high temperature chamber via the regenerator. A first sleeve is fixed within the lower part of the low temperature cylinder to surround part of the displacer body. A second sleeve is fixed below the high temperature chamber. The displacer rod extends through the second sleeve and into a spring chamber. A plurality of flat displacer suspension springs (see Fig. 18) are mounted within the spring chamber to support the displacer so as to prevent rubbing contact of the displacer with the first sleeve and the second sleeve and thus, wear of the displacer and the sleeves as the displacer is reciprocated. Each of the displacer suspension springs is in the form of a circular disk and has a plurality of spiral slits to provide a plurality of spiral arms. The spiral arms 30a are vertically deflected as the displacer is reciprocated. A plurality of annular outer retainers are secured to the inner wall of the spring chamber to sandwich the outer peripheral edges of the displacer suspension springs. Similarly, a plurality of annular inner retainers are secured to the displacer rod to sandwich the inner peripheral edges of the displacer suspension springs. In this arrangement, however, the spiral arms are susceptible to fatigue failure as a result of periodic application of local stresses during the normal operation of the displacer. This is due to the fact that the inner and outer ends of the spiral arms are held substantially in point contact with the circumferential edges of the inner and outer retainers (see Fig. 19) and subject to high stress concentration as the spiral arms are deflected. It is an object of the present invention to provide means for supporting piston/displacer for use in a cryogenic refrigerator, characterized by lower local stresses and reduced susceptibility to fatigue failure so as to increase the service life of the overall cryogenic refrigerator. This object is solved by the features of independent claims 1,4,7 and 10. Advantageous modifications of the cryogenic refrigerator according to claim 1 are possible using the features of the subclaims. Objects and features of the present invention will become more clear from the following detailed description of preferred embodiments of the invention when taken in conjunction with the accompanying drawings. Fig. 1 is a side elevational view, in section, of a stirling refrigerator; Fig. 2 is an enlarged view of means for supporting a piston, made according to a first embodiment of the present invention; Fig. 3 is a plan view of Fig. 2, showing one form of outer retainers (only one is shown) between which piston suspension springs are inserted; Fig. 4 is a view similar to Fig. 3, but showing a modified form of the outer retainers (only one is shown); Fig. 5 is an enlarged view of means for supporting a displacer, made according to a second embodiment of the present invention; Fig. 6 is a plan view of Fig. 5, showing one form of outer retainers (only one is shown) between which displacer suspension springs are inserted; Fig. 7 is a view similar to Fig. 6, but showing a modified form of the outer retainers (only one is shown); Fig. 8 is an enlarged view of means for supporting a piston, made according a third embodiment of the present invention; Fig. 9 is a plan view of Fig. 8, showing one form of inner retainers (only one is shown) between which piston suspension springs are inserted; Fig. 10 is a view similar to Fig. 9, but showing a modified form of the inner retainers (only one is shown); Fig. 11 is an enlarged view of means for supporting a displacer, made according a fourth embodiment of the present invention; Fig. 12 is a plan view of Fig. 11, showing one form of inner retainers (only one is shown) between which displacer suspension springs are inserted; Fig. 13 is a view similar to Fig. 12, but showing a modified form of the inner retainers (only one is shown); Fig. 14 is a plan view of means for supporting a piston not belonging to the present invention; Fig. 15 is a plan view of means for supporting a displacer not belonging to the present invention; Fig. 16 is a plan view of a piston suspension spring known in the art; Fig. 17 is a plan view of the piston suspension spring of Fig. 16 cooperating with inner and outer retainers to support a piston; Fig. 18 is a plan view of a displacer suspension spring known in the art; and Fig. 19 is a plan view of the displacer suspension spring of Fig. 18 cooperating with inner and outer retainers to support a displacer. Like reference numerals designate like or corresponding parts throughout several views of the drawing. Referring now to Fig. 1, a stirling refrigerator 10 generally comprises a compressor 12, and a cold finger 14 connected to the compressor 12 through a conduit 16. The compressor 12 includes a compressor housing 18 within which a vertical cylinder 20 is mounted, and a piston 22 mounted for reciprocal motion with a small clearance within the cylinder 20. A plurality of flat piston suspension springs 24 are arranged within the compressor housing 18 to support the piston 22 so as to prevent rubbing contact of the piston 22 with the inner wall of the cylinder 20 and thus, wear of the piston 22 and the cylinder 20. As better shown in Figs. 2 and 3, each of the piston suspension springs 24 is in the form of a circular disk and includes one or more spiral slits 24a to provide spiral arms 24b. The spiral arms 24b are vertically deflected as the piston 22 is reciprocated within the cylinder 20. A plurality of annular outer retainers 30 are secured to the inner wall of the housing 18 and arranged to sandwich the outer peripheral edges of the piston suspension springs 24. Similarly, a plurality of annular inner retainers 30 are secured to a piston rod 22a and arranged to sandwich the inner peripheral edges of the piston suspension springs 24. Referring again to Fig. 1, a moving coil 36 is mounted to the piston rod 22a and includes a cylindrical bobbin 38 made from a non-magnetic material, and an electrically conductive wire 40 wound around the bobbin 38. A pair of lead wires 42 and 42 have one ends connected to ends of the electrically conductive wire 40 and the other ends connected to a corresponding pair of terminals 44 and 44. A permanent magnet 46 and a yoke 48 are mounted within the housing 18 and jointly form a magnetic circuit. The magnetic circuit has a space 50 within which the moving coil 36 is free to reciprocate in the axial direction of the piston 22. A permanent magnetic field is formed horizontally within the space 50. A high pressure working gas such as helium gas is filled in the interior of the compressor 12. A compression chamber 52 is defined above the piston 22 within the cylinder 20. The piston 22 and the cylinder 20 are arranged to form as small an annular clearance as possible to substantially prevent the passing of working gas between the piston 22 and the cylinder 20. The cold finger 14 includes a low temperature cylinder 55 within which a displacer 57 is reciprocally moved. The displacer 57 has a body 57a and a rod 57b extending downwardly from the body 57a. The interior of the low temperature cylinder 55 is divided by the displacer 57 into two chambers, namely, a low temperature chamber 59 above the displacer 57, and a high temperature chamber 61 below the displacer body 57a. A regenerator 63 is mounted within the displacer body 57a. A gas port 65 is formed in the displacer body 57a to provide a fluid communication between the lower temperature chamber 59 and the high temperature chamber 61 via the regenerator 63. The regenerator 63 is filled with regenerative material such as gauze disks 67 made of copper. A first sleeve 69 is fixed within the lower part of the low temperature cylinder 55 to surround part of the displacer body 57a. A second sleeve 71 is fixed below the high temperature chamber 61. The displacer rod 57b extends through the second sleeve 71 and into a spring chamber 73. A high pressure working gas such as helium gas as in the compressor 12 is filled in the various chambers of the cold finger 14. The displacer body 57a and the first sleeve 69 are arranged to form as small an annular clearance as possible to substantially prevent the passing of working gas between the displacer body 57a and the first sleeve 69. Similarly, the displacer rod 57b and the second sleeve 71 are arranged to form as small an annular clearance as possible to substantially prevent the passing of working gas between the displacer rod 57b and the second sleeve 71. A plurality of flat displacer suspension springs 75 are mounted within the spring chamber 73 to support the displacer 57 so as to prevent rubbing contact of the displacer 57 with the first sleeve 69 and the second sleeve 71 and thus, wear of the displacer 57 and the sleeves 69 and 71 as the displacer 57 is reciprocated through the first sleeve 69 and the second sleeve 71. As better shown in Figs. 5 and 6, each of the displacer suspension springs 75 is in the form of a circular disk and has a plurality of spiral slits 75a to provide spiral arms 75b. The spiral arms 75b are vertically deflected as the displacer 57 is reciprocated. A plurality of annular outer retainers 77 are secured to the inner wall of the spring chamber 73 to sandwich the outer peripheral edges of the displacer suspension springs 75. Similarly, a plurality of annular inner retainers 79 are secured to the displacer rod 57b to sandwich the inner peripheral edges of the displacer suspension springs 75. The compression chamber 52 of the compressor 12 is connected through the conduit 16 to the high temperature chamber 61 of the cold finger 14. The compression chamber 52, the conduit 16, the low temperature chamber 59, the high temperature chamber 61, the regenerator 57, and the gas port 65 are all communicated with one another and jointly form a working chamber. In operation, an alternating current is applied to the electrically conductive wire 40 through the terminal 44 and the lead wire 42. This develops Lorentz's force in the axial direction of the electrically conductive wire 40 of the moving coil 36 as a result of interaction between the alternating current and the magnetic field in the space 50. The piston 22 is then oscillated or reciprocated within the compressor cylinder 20 under the action of the piston suspension springs 24 to cause sinusoidal oscillation of pressure of gas in the working chamber from the compression chamber 52 to the low temperature chamber 59. The second sleeve 71 and the displacer rod 57b is arranged to enable the dimension of annular clearance to be so small that an effective clearance seal can be set up. However, such an clearance seal may be lost after the piston is operated over a period of time. This causes pressure in the spring chamber 73 to be kept approximately at an intermediate level between the maximum and minimum pulsating outputs of the piston 22. When the pulsating output from the piston 22 is transmitted to the high temperature chamber 61, vertical load is exerted on the displacer 57. The load is represented by the difference between the pressures in the high temperature chamber 61 and the spring chamber 73 multiplied by the cross sectional area of the displacer rod 57b. Under this load as well as action of the displacer suspension springs 75, the displacer 57 is vertically oscillated within the cold finger 14 at the same frequency, but 90 degrees out of phase from the piston 22. When the displacer 57 is positioned within the upper part of the cold finger 14, the piston 22 is moved up to compress a working gas in the overall working chamber. A working gas in the compression chamber 52 then flows through the conduit 16 to the high temperature chamber 61. The heat as generated when the working gas is compressed is dissipated to the atmosphere through the housing 18 and the conduit 16. The displacer 57 is then moved down to cause the working gas within the high temperature chamber 61 to flow through the regenerator 63 and the gas port 65 to the low temperature chamber 59. At this time, the working gas is cooled in the regenerator 63. The piston 22 is thereafter moved down to expand the working gas in the overall working chamber. The working gas in the low temperature chamber 59 is also expanded. This results in a decrease in the temperature of the working gas in the low temperature chamber 59. The displacer 57 is next moved up to cause the working gas in the low temperature chamber 59 to flow through the regenerator 63 and the gas port 65 to the high temperature chamber 61. At this time, the regenerator 63 is cooled. The piston 22 is again moved up to compress the working gas. The same cycle of operation is then repeated. The working gas generates heat when it is compressed upon upward motion of the piston 22 and absorbs heat from outside when it is expanded upon downward motion of the piston 22. As explained above, the working gas is expanded when the displacer 57 is positioned within the upper part of the cold finger 14 or when the volume of the low temperature chamber 59 is small. Conversely, the working gas is expanded when the displacer 57 is positioned within the lower part of the cold finger 14 or when the volume of the low temperature chamber 59 is large. Thus, the low temperature chamber 59 is mainly subjected to gas expansion during each cycle of operation and absorb heat from one end of the cold finger to cool an object. Referring again to Fig. 3, each of the annular outer retainers 30 includes a plurality of projections 30a. The projections 30a extend inwardly from the outer ends of the spiral slits 24a so as to sandwich the outer ends of the spiral arms 24b of the piston suspension spring 24. Each of the projections 30a has one side 30b extending radially of the piston suspension spring 24 to make a linear contact with the corresponding spiral arm 24b. This arrangement, linear contact rather than point contact as in the prior art, reduces the local stress intensity at the outer ends of the spiral arms 24b when the spiral arms 24b are periodically deflected. Alternatively, an annular outer retainer 31 may have projections 31a extending inwardly from the outer ends of the spiral slits 24a to sandwich the outer ends of the spiral arms 24b, and each of the projections 31a may extend obliquely to the radial direction of the piston suspension spring 24 as shown in Fig. 4. Referring to Fig. 6, each of the annular outer retainers 77 includes a plurality of projections 77a. The projections 77a extend inwardly from the outer ends of the spiral slits 75a so as to sandwich the outer ends of the spiral arms 75b of the displacer suspension spring 75. Each of the projections 77a has one side 77b extending radially of the displacer suspension spring 75 to make a linear contact with the corresponding spiral arm 75b. This arrangement, linear contact rather than point contact as in the prior art, reduces the local stress intensity at the outer ends of the spiral arms 75b when the spiral arms 75b are periodically deflected. Alternatively, an annular outer retainer 78 may have projections 78a extending inwardly from the outer ends of the spiral slits 75a to sandwich the outer ends of the spiral arms 75b, and each of the projections 78a may extend obliquely to the radial direction of the displacer suspension spring 75 as shown in Fig. 7. Referring to Fig. 9, each of the annular inner retainers 80 includes a plurality of projections 80a. The projections 80a extend outwardly from the inner ends of the spiral slits 24a so as to sandwich the inner ends of the spiral arms 24b of each piston suspension spring 24. Each of the projections 80a has one side 80b extending radially of the piston suspension spring 24 to make a linear contact with the corresponding spiral arm 24b. This arrangement, linear contact rather than point contact as in the prior art, reduces the local stress intensity at the inner ends of the spiral arms 24b when the spiral arms 24b are periodically deflected. Alternatively, an annular inner retainer 81 may have projections 81a extending outwardly from the inner ends of the spiral slits 24a to sandwich the inner ends of the spiral arms 24b, and each of the projections 81a may extend obliquely to the radial direction of the piston suspension spring 24. Referring to Fig. 12, each of the annular inner retainers 84 includes a plurality of projections 84a. The projections 84a extend outwardly from the inner ends of the spiral slits 75a so as to sandwich the inner ends of the spiral arms 75b of the displacer suspension spring 75. Each of the projections 84a has one side 84b extending radially of the displacer suspension spring 75 to make a linear contact with the corresponding spiral arm 75b. This arrangement, linear contact rather than point contact as in the prior art, reduces the local stress intensity at the inner ends of the spiral arms 75b when the spiral arms 75b are periodically deflected. Alternatively, an annular inner retainer 85 may have projections 85a extending outwardly from the inner ends of the spiral slits 75a to sandwich the inner ends of the spiral arms 75b, and each of the projections 85a may extend obliquely to the radial direction of the displacer suspension spring 75. Referring to Fig. 14, a piston suspension spring 90 has a plurality of spiral slits 90a to provide a plurality of spiral arms 90b. In this embodiment, the piston suspension spring 90 includes a plurality of apertures 90c. The inner and outer ends of the spiral slits 90a extend tangentially of and terminate at the corresponding apertures 90c. The apertures 90c are located between the inner and outer ends of the spiral slits 90a and the inner and outer retainers 32 and 82, respectively. This arrangement is intended to reduce the local stress intensity at the inner and outer ends of the spiral arms 90b by distributing stresses along the apertures 90c when the spiral arms 90b are periodically deflected. Referring to Fig. 15, a displacer suspension spring 92 has a plurality of spiral slits 92a to provide a plurality of the spiral arms 92b. In the illustrated embodiment, the displacer suspension spring 92 includes a plurality of apertures 92c. The inner and outer ends of the spiral slits 92a extend tangentially of and terminate at the corresponding apertures 92c. The apertures 92c are located between the inner and outer ends of the spiral slits and the inner and outer retainers 79 and 86, respectively. This arrangement is also intended to reduce the local stress intensity at the inner and outer ends of the spiral arms 92b by distributing stresses along the apertures 92c when the spiral arms 92b are periodically deflected.

Claims: Cryogenic refrigerator (10) comprising a compressor (12) including a compressor housing (18), a cylinder (20) mounted within said housing (18), a piston (22) reciprocable within said cylinder (20), and a compression chamber (52) defined in said cylinder (20) and having a variable volume, and a cold finger (14) including a low temperature cylinder (55), a displacer (57) reciprocable within said low temperature cylinder (55) and adapted to divide the interior of said low temperature cylinder (55) into a low temperature chamber (59) and a high temperature chamber (61), a regenerator (63) mounted within said displacer (57), and means for supporting said piston (22) including at least one flat piston suspension spring (24) having inner and outer peripheral edges and a plurality of spiral slits (24a) to provide a plurality of spiral arms (24b) deflectable as said piston (22) is reciprocated within said compressor cylinder (20), each of said plurality of spiral arms (24b) having inner and outer ends; a plurality of annular inner retainers (32) secured to said piston (22) and adapted to sandwich the inner peripheral edge of said at least one piston suspension spring (24); and a plurality of annular outer retainers (30,31) secured to said compressor housing (18), characterized in that said plurality of annular outer retainers (30,31) include a plurality of projections (30a,31a) extending inwardly over the full width of the outer ends of said spiral arms (24b) to sandwich the outer ends of said spiral arms (24b) in said at least one flat piston suspension spring (24), the number of said projections (30a,31a) corresponding to the number of spiral arms (24b). Refrigerator according to claim 1, wherein each of said plurality of projections (30a) has one side (30b) extending radially of said at least one flat piston suspension spring (24). Refrigerator according to claim 1, wherein each of said plurality of projections (31a) has one side (31b) extending obliquely to the radial direction of said at least one flat piston suspension spring (24). Cryogenic refrigerator (10) comprising a compressor (12) including a compressor housing (18), a cylinder (20) mounted within said housing (18), a piston (22) reciprocable within said cylinder (20), and a compression chamber (52) defined in said cylinder (20) and having a variable volume, and a cold finger (14) including a low temperature cylinder (55), a displacer (57) reciprocable within said low temperature cylinder (55) and adapted to divide the interior of said low temperature cylinder (55) into a low temperature chamber (59) and a high temperature chamber (61), a regenerator (63) mounted within said displacer (57), and means for supporting said piston (22), including at least one flat piston suspension spring (24) having inner and outer peripheral edges, a plurality of spiral slits (24a) to provide a plurality of spiral arms (24b) deflectable as said piston (22) is reciprocated within said compressor cylinder (20), each of said plurality of spiral arms (24b) having inner and outer ends; a plurality of annular outer retainers (82) secured to said compressor housing (18) and adapted to sandwich the outer peripheral edge of said at least one piston suspension spring (24); and a plurality of annular inner retainers (80,81) to said piston (22), characterized in that said plurality of annular inner retainers (80,81) include a plurality of projections (80a,81a) extending outwardly over the full width of the inner ends of said spiral arms (24b) to sandwich the inner ends of said spiral arms (24b) in said at least one flat piston suspension spring (24), the number of said projections (80a,81a) corresponding to the number of spiral arms (24b). Refrigerator according to claim 4, wherein each of said plurality of projections (80a) has one side (80b) extending radially of said at least one flat piston suspension spring (24). Refrigerator according to claim 4, wherein each of said plurality of projections (81a) has one side (81b) extending obliquely to the radial direction of said at least one flat piston suspension spring (24). Cryogenic refrigerator (10) comprising a compressor (12) including a compressor housing (18), a cylinder (20) mounted within said housing (18), a piston (22) reciprocable within said cylinder (20), and a compression chamber (52) defined in said cylinder (20) and having a variable volume, and a cold finger (14) including a low temperature cylinder (55), a displacer (57) reciprocable within said low temperature cylinder (55) and adapted to divide the interior of said low temperature cylinder (55) into a low temperature chamber (59) and a high temperature chamber (61), a regenerator (63) mounted within said displacer (57), a spring chamber (73) extending from said low temperature cylinder (55), and means for supporting said displacer (57) including at least one flat displacer suspension spring (75) having inner and outer peripheral edges and a plurality of spiral slits (75a) to provide a plurality of spiral arms (75b) deflectable as said displacer (57) is reciprocated within said low temperature cylinder (55), each of said plurality of spiral arms (75b) having inner and outer ends; a plurality of annular inner retainers (79) secured to said displacer (57) and adapted to sandwich the inner peripheral edge of said at least one displacer suspension spring (75); and a plurality of annular outer retainers (77,78) secured to said spring chamber (73), characterized in that said plurality of annular outer retainers (77,78) include a plurality of projections (77a,78a) extending inwardly over the full width of the outer ends of said spiral arms (24b) to sandwich the outer ends of said spiral arms (24b) in said at least one flat displacer suspension spring (75), the number of said projections (77a,78a) corresponding to the number of spiral arms (24b). Refrigerator according to claim 7, wherein each of said plurality of projections (77a) has one side (77b) extending radially of said at least one flat displacer suspension spring (75). Refrigerator according to claim 7, wherein each of said plurality of projections (78a) has one side (78b) extending obliquely to the radial direction of said at least one flat displacer suspension spring (75). Cryogenic refrigerator (10) comprising a compressor (12) including a compressor housing (18), a cylinder (20) mounted within said housing (18), a piston (22) reciprocable within said cylinder (20), and a compression chamber (52) defined in said cylinder (20) and having a variable volume, and a cold finger (14) including a low temperature cylinder (55), a displacer (57) reciprocable within said low temperature cylinder (55) and adapted to divide the interior of said low temperature cylinder (55) into a low temperature chamber (59) and a high temperature chamber (61), a regenerator (63) mounted within said displacer (57), a spring chamber (73) extending from said low temperature cylinder (55), and means for supporting said displacer (57) including a least one flat displacer suspension spring (75) having inner and outer peripheral edges a plurality of spiral slits (75a) to provide a plurality of spiral arms (75b) deflectable as said displacer (57) is reciprocated within said low temperature cylinder (55), each of said plurality of spiral arms (75b) having inner and outer ends; a plurality of annular outer retainers (86) secured to said low temperature cylinder (55) and adapted to sandwich the outer peripheral edge of said at least one displacer suspension spring (75); and a plurality of annular inner retainers (84,85) secured to said displacer (57), characterised by said plurality of annular inner retainers (84,85) including a plurality of projections (84a,85a) extending outwardly over the full width of the inner ends of said spiral arms (75b) to sandwich the inner ends of said spiral arms (75b) in said at least one flat displacer suspension spring (75), the number of said projections (84a,85a) corresponding to the number of spiral arms (75b). Refrigerator according to claim 10, wherein each of said plurality of projections (84a) has one side (84b) extending radially of said at least one flat displacer suspension spring (75). Refrigerator according to claim 10, wherein each of said plurality of projections (85a) has one side (85b) extending obliquely to the radial direction of said at least one flat displacer suspension spring (75).

Inventors: FUJII NOBUO C O MITSUBISHI DEN, KATAGISHI YOSHIHIRO C O MITSUB, KIYOTA HIROYUKI C O MITSUBISHI, MIYAZAWA TAKESHI C O MITSUBISH, NIITSU KAZUKI C O MITSUBISHI S, OHISHI TATSURU C O MITSUBISHI, FUJII, NOBUO C/O MITSUBISHI DENKI K.K., KATAGISHI,YOSHIHIRO C/O MITSUBISHI DENKI ENG. K.K., KIYOTA, HIROYUKI C/O MITSUBISHI DENKI K.K., MIYAZAWA, TAKESHI C/O MITSUBISHI DENKI ENG. K.K., NIITSU, KAZUKI, C/O MITSUBISHI SPACE SOFTWARE K.K., OHISHI, TATSURU, C/O MITSUBISHI DENKI K.K.
Applicants: MITSUBISHI ELECTRIC CORP, MITSUBISHI DENKI KABUSHIKI KAISHA
Application year: 1993
Main classification: F25B9
IPC codes: F04B35, F25B9