EP3409944A1 - Compresseur hermétique et procédé de production d'un compresseur hermétique - Google Patents

Compresseur hermétique et procédé de production d'un compresseur hermétique Download PDF

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Publication number
EP3409944A1
EP3409944A1 EP18171772.9A EP18171772A EP3409944A1 EP 3409944 A1 EP3409944 A1 EP 3409944A1 EP 18171772 A EP18171772 A EP 18171772A EP 3409944 A1 EP3409944 A1 EP 3409944A1
Authority
EP
European Patent Office
Prior art keywords
center
cylindrical member
outer circumferential
housing
flat surface
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Withdrawn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
EP18171772.9A
Other languages
German (de)
English (en)
Inventor
Youhei Hotta
Yoshiyuki Kimata
Hajime Sato
Masashi Hamano
Kosuke Nakamura
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.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems Ltd
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 Mitsubishi Heavy Industries Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP3409944A1 publication Critical patent/EP3409944A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/803—Electric connectors or cables; Fittings therefor

Definitions

  • the present invention relates to airtight compressors and methods of producing hermetic compressors.
  • Some compressors are installed in air conditioning devices, refrigerating devices, and the like provided with refrigeration circuits through which refrigerant circulates.
  • those with a compressing mechanism and an electric motor installed in an airtight container are also referred to as hermetic compressors.
  • the compressing mechanism installed in the hermetic compressor is of, for example, scroll type or rotary type, and one or more compressing mechanisms may be mounted on a rotating shaft.
  • the housing of the hermetic compressor usually has a cylindrical shape, and thus the outer circumferential surface thereof is curved.
  • the housing is provided with connecting terminals for supplying power to the electric motor installed in the housing.
  • the connecting terminals are secured to the housing by welding.
  • a flat surface is formed in the curved outer circumferential surface of the housing by, for example, cutting such that welding electrodes can closely adhere to the surface during welding.
  • Patent Literature 1 described below discloses a technology regarding an airtight container in which compressor components (compressing mechanism) of a scroll compressor are installed.
  • a flat surface to which connecting terminals are resistance welded is formed in the body of the airtight container on the outer side of the inner circumferential surface of the body.
  • the housing of hermetic compressors known in the art has been cylindrical, and the cross-sectional shape obtained by cutting the housing in a direction perpendicular to the axial direction has a predetermined thickness.
  • the center of the outer surface and the center of the inner surface of the cylindrical housing correspond to each other.
  • the cylindrical member of the housing may be produced by bending a steel element into a cylindrical shape and then by welding the opposing faces of the steel element to each other.
  • the housing is produced by machining a general-purpose (commercial) cylindrical steel pipe.
  • the housing made of the steel pipe, which is integrally molded, can withstand high pressure compared with the case where a steel element is bent and welded.
  • the outer diameters and the thicknesses of general-purpose steel pipes are defined in accordance with standards such as Japanese Industrial Standards (JIS).
  • JIS Japanese Industrial Standards
  • a flat surface formed in the outer circumferential surface of the above-described housing is located on the inner side of the outer circumferential surface of the housing, and thus the thickness of the housing at the flat surface is smaller than the thickness of the other part.
  • the cylindrical member Since the cylindrical member is reduced in thickness at the flat surface of the housing to which the connecting terminals are connected, the cylindrical member has a lower strength at the flat surface and thus readily deforms. This reduces the reliability of the housing as a pressure vessel.
  • the cylindrical member needs to be formed using a steel pipe that does not conform to standards such as JIS or a steel pipe that is not distributed as a general-purpose product. In a case where a steel pipe distributed as a general-purpose product is used, a large steel pipe needs to be chosen and cut from the outer circumferential surface thereof to obtain a housing with a desired thickness.
  • An object of the present invention is to provide a hermetic compressor, including a cylindrical member with a flat surface formed in the outer circumferential surface thereof and prevented from deforming, thereby ensuring the reliability more readily.
  • Another object of the present invention is to provide a method of producing the hermetic compressor.
  • a hermetic compressor includes a housing including a cylindrical member.
  • the cylindrical member includes an outer surface of which cross-section obtained by cutting the cylindrical member in a direction perpendicular to an axial direction has an outer circumferential surface with a predetermined outer diameter and a cylindrical inner surface of which cross-section of the cylindrical member has a predetermined inner diameter.
  • the outer surface includes a flat surface located closer to a center of the outer circumferential surface than the outer circumferential surface is.
  • a center of the inner surface of the cylindrical member is located on a side of the center of the outer circumferential surface of the cylindrical member opposite the side on which the flat surface lies.
  • the housing includes the cylindrical member.
  • the outer surface of the cylindrical member having the outer circumferential surface with the predetermined outer diameter includes the flat surface located closer to the center of the outer circumferential surface than the outer circumferential surface of the cylindrical member is, and the inner surface of the cylindrical member has the predetermined inner diameter.
  • the center of the inner surface of the cylindrical member is located on the side of the center of the outer circumferential surface of the cylindrical member opposite the side on which the flat surface lies.
  • the cylindrical member is made thick at a portion corresponding to the flat surface compared with a case where the center of the outer surface and the center of the inner surface of the cylindrical member correspond to each other. This increases the strength of the cylindrical member, and prevents deformation.
  • a thickness of a thinnest portion between the outer surface and the inner surface at the flat surface formed in the outer surface may be equal to a thickness of a thinnest portion between the outer surface and the inner surface on a side remote from the flat surface formed in the outer surface.
  • the stress acting on the thinnest portion between the outer surface and the inner surface at the flat surface formed in the outer surface and the stress acting on the thinnest portion between the outer surface and the inner surface on the side remote from the flat surface formed in the outer surface can be substantially equal.
  • the flat surface formed in the outer surface may have a through-hole, and a connecting terminal electrically connected to an electric motor may be secured to the through-hole.
  • the through-hole is formed in the flat surface formed in the outer surface, and the connecting terminal electrically connected to the electric motor is secured to the through-hole.
  • the connecting terminal is secured to the through-hole in the flat surface formed in the outer surface, the securing portion of the connecting terminal is thick enough to ensure the strength.
  • the hermetic compressor including a housing including a cylindrical member, the cylindrical member including an outer surface of which cross-section obtained by cutting the cylindrical member in a direction perpendicular to an axial direction has an outer circumferential surface with a predetermined outer diameter and a cylindrical inner surface of which cross-section of the cylindrical member has a predetermined inner diameter, includes forming a flat surface in the outer surface at a position closer to a center of the outer circumferential surface than the outer circumferential surface is; and forming the inner surface such that a center of the inner surface of the cylindrical member is located on a side of the center of the outer circumferential surface of the cylindrical member opposite the side on which the flat surface lies.
  • a cylindrical member including a flat surface formed in the outer circumferential surface thereof is prevented from deforming, thereby ensuring the reliability more readily.
  • a hermetic compressor according to an embodiment of the present invention is applied to an airtight multistage compressor for an air conditioning device or a refrigerating device.
  • the present invention is applied to an airtight multistage compressor (multistage compressor) 1 including a rotary compressor 2 at a lower stage and a scroll compressor 3 at a higher stage as an example.
  • multistage compressor multistage compressor
  • the present invention is also applicable to, for example, single-stage scroll compressors or multistage scroll compressors including scroll compressors at both the lower and higher stages.
  • the multistage compressor 1 provided with the rotary compressor 2 and the scroll compressor 3 includes an airtight housing 10.
  • the airtight housing 10 includes a cylindrical center housing 10A, a bearing member 31 swaged to an upper portion of the center housing 10A, a lower housing 10B hermetically sealing a lower portion of the center housing 10A, and an upper housing 10C welded to the entire circumference of the center housing 10A above the bearing member 31 to hermetically seal the upper portion of the center housing 10A.
  • An electric motor 4 including a stator 5 and a rotor 6 is securely installed inside the center housing 10A substantially in a central area of the center housing 10A.
  • a rotating shaft (crankshaft) 7 is integrated with the rotor 6.
  • the rotary compressor 2 at the lower stage is disposed below the electric motor 4.
  • the rotary compressor 2 at the lower stage includes a cylinder body 21 provided with a cylinder chamber 20 and secured inside the center housing 10A, an upper bearing 22 secured to the top of the cylinder body 21 to hermetically seal the upper portion of the cylinder chamber 20, a lower bearing 23 secured to the bottom of the cylinder body 21 to hermetically seal the lower portion of the cylinder chamber 20, a rotor 24 engaging with a crank portion 7A of the rotating shaft 7 and rotatable on the inner circumferential surface of the cylinder chamber 20, blades (not illustrated) partitioning the cylinder chamber 20 into a suction side and a discharge side, blade retaining springs, and other components.
  • the rotary compressor 2 first sucks low-pressure refrigerant gas into the cylinder chamber 20 via a suction pipe 25, and compresses the refrigerant gas to an intermediate pressure using the rotation of the rotor 24.
  • the rotary compressor 2 then discharges the resultant refrigerant gas into a discharge chamber 26 formed above the cylinder chamber 20 using the upper bearing 22 and into a discharge chamber 27 formed below the cylinder chamber 20 using the lower bearing 23.
  • the refrigerant gas then joins in the discharge chamber 26, and is discharged into the center housing 10A.
  • the intermediate-pressure refrigerant gas is led through a gas channel or other paths formed in the rotor 6 of the electric motor 4 to a space above the electric motor 4, and is sucked into the scroll compressor 3 at the higher stage to be further compressed.
  • the scroll compressor 3 at the higher stage is disposed inside the upper housing 10C.
  • the scroll compressor 3 includes the bearing member 31 provided with a bearing 30 supporting the rotating shaft (crankshaft) 7, a fixed scroll member 32 including a spiral lap 32B extending from an end plate 32A, and an orbiting scroll member 33 including a spiral lap 33B extending from an end plate 33A.
  • the fixed scroll member 32 and the orbiting scroll member 33 constitute a pair of compression chambers 34 by engaging and mounting the spiral laps 32B and 33B on the bearing member 31.
  • the scroll compressor 3 further includes an orbiting boss 33C joining the orbiting scroll member 33 and an eccentric pin 7B of the rotating shaft 7 via a drive bush 13 to drive the orbiting scroll member 33 to revolve, a rotation prevention mechanism 35 disposed between the orbiting scroll member 33 and the bearing member 31 and preventing the orbiting scroll member 33 from rotating to drive the orbiting scroll member 33 to revolve, a discharge valve 36 formed at the rear side of the fixed scroll member 32 to open and close a discharge port 32C, a discharge cover 38 secured to the rear side of the fixed scroll member 32 to surround the discharge valve 36, and a discharge pipe 39 connected to the central portion of the discharge cover 38 to discharge compressed high-temperature high-pressure gas to the outside.
  • the rotary compressor 2 disposed at the lower stage compresses and discharges refrigerant gas at the intermediate pressure to the airtight housing 10, and the scroll compressor 3 sucks the refrigerant gas into the compression chambers 34.
  • the scroll compressor 3 then further compresses the intermediate-pressure refrigerant gas to a higher pressure using compression movement of the orbiting scroll member 33 that is driven to revolve, and discharges the resultant gas into the inside of the discharge cover 38 via the discharge valve 36.
  • the high-temperature high-pressure refrigerant gas is sent to the outside of the multistage compressor 1, that is, to the refrigerating cycle via the discharge pipe 39.
  • a known displacement oil pump 14 is disposed between the lowest end portion of the rotating shaft (crankshaft) 7 and the lower bearing 23 of the rotary compressor 2 disposed at the lower stage.
  • the displacement oil pump 14 draws up lubricant 15 filling the bottom portion of the airtight housing 10, and forcibly supplies the lubricant 15 to portions that require lubrication such as bearing portions of the rotary compressor 2 and the scroll compressor 3 through oil supply holes formed in the rotating shaft 7.
  • a through-hole 41 is formed in a flat surface 40 formed in an outer surface 42 of the center housing 10A.
  • a connecting terminal 50 is secured to the through-hole 41, and is electrically connected to the electric motor 4.
  • the connecting terminal 50 supplies power to the built-in electric motor 4 via a cable 53.
  • the connecting terminal 50 includes a support portion 51 and a terminal portion 52 secured to the support portion 51. At the flat surface 40, the support portion 51 of the connecting terminal 50 is securely welded to the through-hole 41.
  • the center housing 10A of the airtight housing 10 will now be described in detail.
  • the center housing 10A of the airtight housing 10 is a cylindrical member having a hollow cylindrical shape and a predetermined length in the axial direction.
  • the center housing 10A is produced by, for example, machining a general-purpose (commercial) cylindrical steel pipe defined by standards such as JIS.
  • the steel pipe is integrally molded, and thus the center housing 10A can withstand high pressure compared with the case where the steel pipe is produced by bending and welding a steel element.
  • the steel pipe used for producing the center housing 10A has, for example, the JIS nominal diameter of 125A, that is, an outer diameter of 139.8 mm, and has the nominal thickness of Schedule 80, that is, a thickness of 9 mm.
  • the center housing 10A serving as a cylindrical member includes the outer surface 42 and an inner surface 43, and has a ring-shaped cross-section as illustrated in Fig. 2 when cut in a direction perpendicular to the axial direction.
  • the outer-circumferential-surface diameter of the outer surface 42 of the center housing 10A that is, the outer diameter is fixed, and the outer circumferential surface is circular in cross section.
  • the flat surface 40 to which the connecting terminal 50 is connected is formed in the outer surface 42 of the center housing 10A. This allows welding electrodes to closely adhere to the flat surface 40 to which the connecting terminal 50 is connected during welding, and thus allows the connecting terminal 50 to be stably welded to the center housing 10A.
  • the flat surface 40 has, for example, a rectangular shape in the outer surface 42 when seen from the front.
  • the flat surface 40 is formed by, for example, cutting the outer circumferential surface of the cylindrical steel pipe.
  • machining for diameter adjustment is not conducted on the outer circumferential surface of the steel pipe during the production of the center housing 10A.
  • the flat surface 40 is formed by cutting the outer circumferential surface of the steel pipe, and thus is located at a position in the center housing 10A closer to the center O 1 of the outer circumferential surface than the outer circumferential surface of the outer surface 42 of the center housing 10A is. In other words, the flat surface 40 is formed on the inner side of the outer circumferential surface of the steel pipe with a fixed outer diameter.
  • the center O 1 of the outer circumferential surface of the center housing 10A does not correspond to the center O 2 of the inner surface 43. Consequently, the outer surface 42 and the inner surface 43 are decentered from each other.
  • the center O 2 of the inner surface 43 is located at a position different from the position of the center O 1 of the outer circumferential surface, and the center O 2 of the inner surface 43 is located on a side of the center O 1 of the outer circumferential surface opposite the side on which the flat surface 40 lies.
  • the thickness of the center housing 10A at a thinnest portion A 3 at a flat surface 80 formed in the outer surface 82 is smaller than the thickness at a thick portion A 4 located opposite the thinnest portion A 3 with the centers O 3 and O 4 interposed therebetween.
  • an inner surface 84 of the steel pipe before cutting is indicated by long dashed double-short dashed lines.
  • the thickness of the center housing 10A at a thinnest portion A 1 at the flat surface 40 formed in the outer surface 42 is thick, and the thickness at a thinnest portion A 2 located opposite the thinnest portion A 1 with the centers O 1 and O 2 interposed therebetween is thin compared with the case where the center O 3 of the outer surface 82 and the center O 4 of the inner surface 83 of the center housing 10A correspond to each other.
  • the center O 1 of the outer circumferential surface and the center O 2 of the inner surface 43 are eccentric to each other, and thus the center housing 10A is made thick at a portion corresponding to the flat surface 40 compared with the case where the center O 3 of the outer surface 82 and the center O 4 of the inner surface 83 of the center housing 10A correspond to each other.
  • This increases the strength of the center housing 10A, and prevents deformation. Consequently, the center housing 10A including the flat surface 40 formed in the outer circumferential surface thereof is prevented from deforming, thereby ensuring the reliability.
  • the inner surface 43 of a general-purpose steel pipe is, for example, cut such that the cross-section of the inner surface 43 of the center housing 10A has a circular shape.
  • an inner surface 44 of the steel pipe before cutting is indicated by long dashed double-short dashed line.
  • the center O 2 of the inner surface 43 is located at a position different from the position of the center O 1 of the outer circumferential surface. More specifically, the inner surface 43 is formed such that the center O 2 of the inner surface 43 is located on a side of the center O 1 of the outer circumferential surface opposite the side on which the flat surface 40 lies. Additionally, cutting or other machining yields a surface smoother than the surface before machining, and increases the accuracy of the circular shape.
  • the thickness of the thinnest portion A 1 having a smallest thickness between the outer surface 42 and the inner surface 43 at the flat surface 40 formed in the outer surface 42 substantially equals to the thickness of the thinnest portion A 2 having a smallest thickness between the outer surface 42 and the inner surface 43 on the side remote from the flat surface 40. This causes the stress acting on the thinnest portion A 1 at the flat surface 40 formed in the outer surface 42 and the stress acting on the thinnest portion A 2 on the side remote from the flat surface 40 formed in the outer surface 42 to be substantially equal.
  • the thickness of the thinnest portion A 1 may be slightly larger than the thickness of the thinnest portion A 2 . This reduces the stress concentrating on the flat surface 40 formed in the outer surface 42.
  • the through-hole 41 is formed in the flat surface 40 formed in the outer surface 42, and the support portion 51 of the connecting terminal 50 is secured to the through-hole 41.
  • the thickness at the flat surface 40 is large enough to prevent deformation compared with the known art, resulting in an increased strength of the securing portion of the connecting terminal 50.
  • the flat surface 40 formed in the outer surface 42 is located closer to the center O 1 than the outer circumferential surface of the center housing 10A is. Additionally, as illustrated in Figs. 2 and 3 , the center O 1 of the outer circumferential surface and the center O 2 of the inner surface 43 are eccentric to each other, and thus the thickness of the center housing 10A at the portion corresponding to the flat surface 40 is larger than that in the known configuration. This increases the strength of the center housing 10A, and prevents deformation. Consequently, the center housing 10A including the flat surface 40 formed in the outer circumferential surface thereof is prevented from deforming, thereby ensuring the reliability.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
EP18171772.9A 2017-05-31 2018-05-11 Compresseur hermétique et procédé de production d'un compresseur hermétique Withdrawn EP3409944A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2017107631A JP2018204453A (ja) 2017-05-31 2017-05-31 密閉型圧縮機及び密閉型圧縮機の製造方法

Publications (1)

Publication Number Publication Date
EP3409944A1 true EP3409944A1 (fr) 2018-12-05

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EP18171772.9A Withdrawn EP3409944A1 (fr) 2017-05-31 2018-05-11 Compresseur hermétique et procédé de production d'un compresseur hermétique

Country Status (2)

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EP (1) EP3409944A1 (fr)
JP (1) JP2018204453A (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5584716A (en) * 1994-07-14 1996-12-17 Copeland Corporation Terminal assembly for hermetic compressor
JPH0914158A (ja) 1995-06-23 1997-01-14 Matsushita Electric Ind Co Ltd スクロール圧縮機およびその製造方法
US20080008608A1 (en) * 2001-09-27 2008-01-10 Sanyo Electric Co., Ltd. Compressor, method for manufacturing the compressor, defroster of refrigerant circuit, and refrigerant unit
US20080173644A1 (en) * 2007-01-22 2008-07-24 Tecumseh Products Company Pressure limiter

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5584716A (en) * 1994-07-14 1996-12-17 Copeland Corporation Terminal assembly for hermetic compressor
JPH0914158A (ja) 1995-06-23 1997-01-14 Matsushita Electric Ind Co Ltd スクロール圧縮機およびその製造方法
US20080008608A1 (en) * 2001-09-27 2008-01-10 Sanyo Electric Co., Ltd. Compressor, method for manufacturing the compressor, defroster of refrigerant circuit, and refrigerant unit
US20080173644A1 (en) * 2007-01-22 2008-07-24 Tecumseh Products Company Pressure limiter

Also Published As

Publication number Publication date
JP2018204453A (ja) 2018-12-27

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