EP2530322A1 - Machine hydraulique - Google Patents

Machine hydraulique Download PDF

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Publication number
EP2530322A1
EP2530322A1 EP11734531A EP11734531A EP2530322A1 EP 2530322 A1 EP2530322 A1 EP 2530322A1 EP 11734531 A EP11734531 A EP 11734531A EP 11734531 A EP11734531 A EP 11734531A EP 2530322 A1 EP2530322 A1 EP 2530322A1
Authority
EP
European Patent Office
Prior art keywords
shell
fluid machine
hermetic container
machine according
driven unit
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Withdrawn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
EP11734531A
Other languages
German (de)
English (en)
Inventor
Noriyuki Kobayashi
Hitomi Ito
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.)
Sanden Corp
Original Assignee
Sanden Corp
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 Sanden Corp filed Critical Sanden Corp
Publication of EP2530322A1 publication Critical patent/EP2530322A1/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Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F04B39/127—Mounting of a cylinder block in a casing
    • 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
    • F04B39/14—Provisions for readily assembling or disassembling
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections

Definitions

  • This invention relates to a fluid machine, specifically a fluid machine suited to form a hermetic reciprocating compressor compressing carbon-dioxide refrigerant.
  • Patent document 1 discloses a hermetic container composed of three members: a center, a top and a bottom shells, the center shell being a steel tube open at each end, and the top and bottom shells being cup-shaped cast members welded to each open end of the center shell.
  • Patent document 2 discloses a hermetic container composed of two press-formed members: top and bottom shells
  • patent document 3 discloses a hermetic container composed of two forged members: top and bottom shells.
  • the aforementioned hermetic containers are each constructed by welding the shells together.
  • the top and bottom shells are cast products, and thus, difficult to weld together and likely to produce poor welds, since cast products have generally a high carbon content.
  • the center shell in the form of a steel tube incurs high material costs.
  • the hermetic container composed of three members requires welding at two locations or more, resulting in correspondingly-increased assembly manhours, and thus, increased cost of producing the hermetic container, and thus, the compressor.
  • the hermetic container composed of two shells, as seen in patent documents 2 and 3, requires welding at fewer locations, and thus, less assembly manhours, leading to a reduced cost of producing the hermetic container.
  • the press-formed or forged shells are expected to alleviate the aforementioned problem of poor welds.
  • press-forming only allows the shells to have a simple shape such as a dome shape, and portions for the electric motor, the compressing mechanism and others to be fixed to need to be created in the shells by additional working, leading to an increase in cost of producing the hermetic container.
  • An object of the present invention is to provide a fluid machine which can be produced with a reduced weight and size at a reduced production cost.
  • a fluid machine comprises a drive unit and a driven unit arranged in a hermetic container such that drive power is transmitted from the drive unit to the driven unit, the hermetic container including a first shell covering the drive unit and a second shell covering the driven unit and joined to the first shell, wherein the first and second shells are members formed by different working processes (claim 1).
  • the first and second shells may be a forged and a press-formed members, respectively (claim 2), or vice versa (claim 3).
  • the fluid machine may be configured such that the drive unit is arranged in the first shell with its length aligned with a depth of the first shell, while the driven unit is arranged in the second shell with its length aligned with a diameter of the second shell (claim 4).
  • the second shell may have a holding portion by which to hold the second shell during forging of the second shell, the holding portion forming a crest of the second shell projecting outward in a central region radially away from a side wall of the second shell (claim 5).
  • the second shell may have a lubricating system configured to supply a lubricant collecting in an inner bottom portion of the second shell to sliding parts of the drive unit and of the driven unit, wherein said inner bottom portion is a recess defined by an inner side of said holing portion and having a shape approximately similar to an outer shape of said holding portion and serving as an oil reservoir (claim 6).
  • the second shell may have a support portion for the drive unit and the driven unit to be fixed to (claim 7).
  • the holding portion, the oil reservoir and the support portion may be parts formed all at once when the second shell is forged (claim 8).
  • the hermetic container may undergo pressure exerted by a working fluid sucked in and discharged from the driven unit, the working fluid being carbon-dioxide refrigerant (claim 9).
  • the fluid machine according to the present invention recited in claim 1 comprises a hermetic container composed of two shells, namely first and second shells, wherein at least either the first or the second shell has a reduced wall thickness since it is formed by press-forming.
  • the hermetic container and thus, the fluid machine have a reduced weight and size.
  • at least the second shell, which is press-formed has a reduced wall thickness
  • at least the first shell, which is press-formed has a reduced wall thickness.
  • the shell formed not by forging is unlikely to produce a poor weld when welded to the other shell.
  • the hermetic container has thus an increased weld strength.
  • the first shell is formed by press-forming to have a depth corresponding to the length of the drive unit
  • the second shell is formed by forging to have a diameter corresponding to the length of the driven unit.
  • the first shell requiring a great depth compared with the second shell, can be easily formed by press-forming into a shape corresponding to the outer shape of the drive unit, with a reduced wall thickness.
  • the second shell not requiring a great depth compared with the first shell, can be easily formed by forging into a shape corresponding to the outer shape of the driven unit, with a reduced wall thickness. This ensures that the hermetic container, and thus, the fluid machine have a reduced weight and size. Further, this allows a reduction of dead space within the hermetic container, leading to a further reduced size of the fluid machine.
  • the holding portion provided to form the crest of the second shell saves the second shell from having an unprofitably-great wall thickness at the side and/or the crest, which would be inevitable when the holding portion is provided at the side of the bottom shell. This leads to a further reduced weight and size of the hermetic container, and thus of the compressor.
  • the provision of the holding portion not only allows a reduction in wall thickness of the second shell but also facilitates provision of an inner bottom portion serving as an oil reservoir, without requiring a separate member such as an oil pan.
  • the inner bottom portion serving as an oil reservoir can hold the lubricant to have an oil surface at a specified level. This ensures that the lubricant is smoothly supplied to the sliding parts through the lubricating system and efficiently circulates within the hermetic container, even though the amount of the lubricant collecting in the inner bottom portion is small.
  • the drive and driven units are easily fixed without requiring another member such as a frame.
  • the holding portion, the oil reservoir and the support portion are easily formed without requiring another member or another working process, which means that the fluid machine can be produced with an increased productivity.
  • the working fluid is carbon-dioxide refrigerant
  • the working fluid is discharged from the driven unit at very high pressure.
  • the inner side of the hermetic container can therefore be subjected to very high pressure, and thus, normally, the hermetic container cannot avoid having a great thickness and weight for safety's sake.
  • the hermetic container and fluid machine structured as described above, which allow effective reduction of weight and size, are therefore favorable.
  • FIGS. 1 to 4 show a compressor 1, a first embodiment of fluid machine.
  • the compressor 1 is a hermetic reciprocating compressor, which belongs to the class of positive-displacement compressors called reciprocating compressors or piston compressors and which is incorporated into, for example an automatic vending machine to constitute a refrigeration cycle circuit, not shown.
  • the refrigeration cycle circuit has a circulation path along which a refrigerant, or working fluid of the compressor 1 circulates.
  • the refrigerant is for example carbon dioxide, which is a non-combustible natural refrigerant.
  • the compressor 1 comprises a hermetic container 2 enclosing an electric motor (drive unit) 4 and a compressing mechanism (driven unit) 6, the latter being supplied with drive power from the former.
  • the electric motor 4 comprises a stator 8 supplied with current to generate a magnetic field, and a rotor 10 rotating in the magnetic field generated by the stator 8.
  • the rotor 10 is arranged within the stator 8, coaxially, and fixed on a main shaft portion 24 of a crankshaft 14, described later, by heat-fitting. Current is supplied to the stator 8 from outside the compressor 1 via electric components 12 fixed to the hermetic container 2 and leads, not shown.
  • the compressing mechanism 6 is composed of a crankshaft 14, a cylinder block 16, a piston 18, a connecting rod 20 and others.
  • the crankshaft 14 includes an eccentric shaft portion 22 and a main shaft portion 24.
  • the cylinder block 16 has a cylinder bore 26.
  • a cylinder gasket 28, a suction valve 50, described later, a valve plate 30, a head gasket 32 and a cylinder head 34, arranged in this order, are fastened to the cylinder block 16 with bolts to close an entrance to the cylinder bore 26.
  • the stator 8 is bolted to the cylinder block 16 with a frame 36 between, the frame 36 being joined to the hermetic container 2.
  • the frame 36 includes a lower base portion 38 joined to the hermetic container 2 and supporting the electric motor 4 and the compressing mechanism 6, and an upper cylindrical portion 40 with a bearing 42 arranged on an inner circumferential face 40a and a bearing 44 on a top face 40b.
  • the bearing 42 supports the main shaft portion 24, and the bearing 44 in the form of a thrust race (bearing), a thrust washer or the like supports a thrust load generated by the rotor 10.
  • the valve plate 30 has a refrigerant suction hole 46 and a refrigerant discharge hole 48 opened and closed by a suction valve 50 and a discharge valve 52, respectively.
  • the suction and discharge valves are reed valves.
  • the cylinder head 34 has a refrigerant suction chamber 54 and a refrigerant discharge chamber 56.
  • the discharge valve 52 opens to allow a flow from the cylinder bore 26 to the discharge chamber 56 through the discharge hole 48.
  • the suction valve 50 opens to allow a flow from the suction chamber 54 to the cylinder bore 26 through the suction hole 46.
  • a suction pipe 58 and a discharge pipe 60 are fitted to the hermetic container 2.
  • the suction and discharge pipes 58, 60 connect to the suction and discharge chambers 54, 56 in the cylinder head 34, at an end, respectively, and to the refrigeration cycle circuit at the other end.
  • Suction and discharge mufflers are incorporated in the suction and discharge pipes to reduce pulsation and noise of the refrigerant flowing therein.
  • the connecting rod 20 has a large end portion 62 connected to the eccentric shaft portion 22 of the crankshaft 14 in a manner allowing rotating motion of the crankshaft, and an opposite small end portion connected to the piston 18 in a manner allowing reciprocating motion of the piston.
  • the small end portion 64 is connected to the piston 18 by a piston pin 66, which is prevented from coming off the piston 18 by a fixing pin 68.
  • the crankshaft 14 has an oil passage (lubricating system) 70 extending approximately from the shaft center at the bottom 22a of the eccentric shaft portion 22 to the middle of the main shaft portion 24.
  • the oil passage 70 has an upper end open at the outer circumferential face 24a of the main shaft portion 24 and a lower end connected to an oil pipe (lubricating system) 72.
  • the oil pipe 72 includes a lower slant portion 74 slanting in a manner approaching the shaft center of the main shaft portion 24 approximately from the shaft center of the eccentric shaft portion 22.
  • the slant portion 74 of the oil pipe 72 extends downward into an inner bottom portion 2a of the hermetic container 2 in the shape of a recess, the inner bottom portion 2a thus serving as an oil reservoir 76.
  • the oil reservoir 76 has an area and a depth ensuring that a small amount of the lubricant, more or less 200 cc, for example, has an oil surface at the level of the lower end of the oil pipe 74 or above.
  • the compressor 1 is designed such that as the stator 8 is supplied with current, the rotor 10 fixed on the main shaft portion 24 rotates, and thus, the crankshaft 14 rotates, which in turn makes the piston 18 reciprocate within the cylinder bore 18 by means of the connecting rod 20. As the piston 18 reciprocates, the refrigerant is sucked into the cylinder bore 26 from the refrigeration cycle circuit, compressed in the cylinder bore 26 and discharged from the cylinder bore to the refrigeration cycle circuit.
  • the piston 18 moves in the direction decreasing the volume of the cylinder bore 26, so that the refrigerant is compressed within the cylinder bore 26.
  • the discharge valve 52 opens because of pressure difference between the cylinder bore 26 and the discharge chamber 56. The refrigerant compressed thus flows from the cylinder bore into the discharge chamber 56 through the discharge hole 48, and then to the refrigeration cycle circuit through the discharge pipe 60.
  • the piston 18 moves in the direction increasing the volume of the cylinder bore 26, and thus, the pressure in the cylinder bore 26 decreases and the discharge valve 50 closes because of pressure difference between the cylinder bore 26 and the discharge chamber 56.
  • the suction valve opens 50 because of pressure difference between the cylinder bore 26 and the suction chamber 54. The refrigerant thus flows into the suction chamber 54 through the suction pipe 58, and then into the cylinder bore 56 through the suction hole 46.
  • the piston 18 moves in the direction decreasing the volume of the cylinder bore 26, and thus, the refrigerant is again compressed within the cylinder bore 26.
  • the process of sucking the refrigerant from the refrigeration cycle circuit into the cylinder bore 26, compressing it within the cylinder bore 26 and discharging it from the cylinder bore to the refrigeration cycle circuit is repeated this way.
  • Part of the lubricant flows out of the oil passage 70 and moves upward along a groove in the circumferential face of the crankshaft 14, not shown, by centrifugal force, thereby forming an oil film between the crankshaft 14 and the frame 36, thus lubricating the bearing 42, and moves further up toward the top of the crankshaft 14.
  • the lubricant flows down into the oil reservoir 76 by gravity.
  • the part of the lubricant not passing over the bearing 44 moves further up the inner wall surface 10a of the rotor 10 to reach the top of the rotor 10, and splashes accompanying the rotation of the rotor 10, by centrifugal force, thus cooling the stator 8, and falls into the oil reservoir 76 by gravity.
  • the hermetic container 2 is a shell structure composed of two shells: a top shell (first shell) 78 covering the electric motor 4 and a bottom shell (second shell) 80 covering the compressing mechanism 6.
  • the crankshaft 14 and the connecting rod 20 need to be arranged at right angles to each other, and thus, the electric motor 4 is arranged in the top shell 78 with its length aligned with the depth of the top shell, while the compressing mechanism 6 is arranged in the bottom shell 80 with its length aligned with a diameter of the bottom shell 80.
  • the top shell 78 has therefore a great depth compared with the bottom shell 80.
  • the shells 78, 80 each have a root edge at their rims 78a, 80a so that the root edges mated form a groove 82.
  • the shells 78, 80 are joined together by forming a weld 84 in the form a continuous series of beads in the groove 82 over its entire length, by a single step of welding. In other words, the shells are joined together by a single butt weld joint formed by a single step of welding.
  • the top shell 78 is formed by press-forming, more specifically deep-drawing a soft steel, such as SPCC or SPHE, into a simple shape like a dome.
  • the top shell 78 is formed as thin as possible, specifically into a thickness of more or less 6.8mm at the thinnest portion and more or less 7mm even at thick portions. Work hardening during deep drawing provides a sufficient resistance to high pressure exerted by the refrigerant.
  • the bottom shell 80 is formed by forging a soft steel, such as S20C or S25C.
  • the bottom shell 80 is formed as thin as possible, specifically into a thickness of more or less 8.5mm.
  • the bottom shell has a sufficient resistance to high pressure exerted by the refrigerant on the hermetic container 2.
  • the bottom shell 80 includes a holding portion 86 by which to hold the bottom shell 80 during forging of the bottom shell 80.
  • the holding portion 86 forms a crest 80c of the bottom shell 80 projecting outward in a central region radially away from a side 80b of the bottom shell 80.
  • the inner bottom portion 2a serving as the oil reservoir 76 is a recess defined by the inner side of the holding portion 86 and having a shape similar to the outer shape of the holding portion 86.
  • the bottom shell 80 has thus an approximately uniform wall thickness throughout the side 80b and the crest 80a.
  • a base plate 88 is fitted around the crest 80a, or holding portion 86 to allow the compressor 1 to be installed stably. Attaching a rubber vibration insulator or the like, not shown, to the underside of the base plate 88 ensures that the compressor 1 is fixed with vibration being reduced during operation.
  • the bottom shell 80 has four support portions 90 bulging radially-inward from the rim 80a and describing an undulating outline.
  • the frame 36 supporting the stator 8 and the cylinder block 16, as seen in FIG. 1 is fixed to these support portions 4.
  • the hermetic container 2 may have another support structure allowing the stator 8 and the cylinder block 16 to be fixed directly to the support portions without a frame 36.
  • the holding portion 86, the oil reservoir 76 and the support portions 90 of the bottom shell 80 are formed all at once when the bottom shell 80 is forged.
  • the above-described compressor 1 presented as a first embodiment of the present invention has a hermetic container 2 composed of two shells 78, 80, wherein at least the press-formed top shell 78 has a reduced wall thickness, resulting in a reduced weight and size of the hermetic container 2, and thus, of the compressor 1.
  • the top shell 78 formed not by forging is unlikely to produce a poor weld when welded to the bottom shell 80, resulting in an increased weld strength of the hermetic container.
  • the top shell 78 is press-formed to have a depth corresponding to the length of the electric motor 4, while the bottom shell 80 is forged to have a diameter corresponding to the length of the compressing mechanism 8.
  • the top shell 78 requiring a great depth compared with the bottom shell 80, can be easily formed by press-forming into a shape corresponding to the outer shape of the electric motor 4, with a reduced wall thickness.
  • the bottom shell 80 not requiring a great depth compared with the top shell 78, can be easily formed by forging into a shape corresponding to the outer shape of the compressing mechanism 6, with a reduced wall thickness. This ensures that the hermetic container 2, and thus, the compressor 1 have a reduced weight and size. Further, this allows a reduction of dead space within the hermetic container 2, leading to a further reduced size of the compressor 1.
  • the holding portion 86 provided to form the crest of the bottom shell 80 saves the bottom shell 80 from having an unprofitably-great wall thickness at the side 80b and/or the crest 80c, which would be inevitable when the holding portion 83 is provided at the side 80b of the bottom shell 80. This leads to a further reduced weight and size of the hermetic container 2, and thus of the compressor 1.
  • the provision of the holding portion 86 not only allows a reduction in wall thickness of the bottom shell 80 but also facilitates provision of an inner bottom portion 2a serving as an oil reservoir 76, without requiring a separate member such as an oil pan.
  • the inner bottom portion 2a serving as an oil reservoir 78 can hold the lubricant to have an oil surface at a specified level.
  • the hermetic container 2 has a support structure allowing the stator 8 and the cylinder block 16 to be fixed directly to the support portions 90 without requiring a frame 36, the electric motor 4 and the compressing mechanism 6 are easily fixed without requiring a separate member such as a frame 36.
  • the holding portion 86, the oil reservoir 76 and the support portions 90 are formed all at once when the bottom shell 80 is forged. In other words, these parts can be easily formed without requiring another member or another working process, which means that the compressor 1 can be produced with an increased productivity.
  • the present invention is not restricted to the above-described embodiment, which can be modified in various ways.
  • the top shell 78 is press-formed and the bottom shell 80 is forged
  • the shells 78, 80 may be formed in another way. What is essential is that the shells 78, 80 be formed by different working processes allowing them to have a reduced wall thickness, and thus, allowing the hermetic container 2, and thus, the compressor 1 to have a reduced weight and size.
  • the described embodiment may be modified such that the top shell 78 is forged and the bottom shell 80 is press-formed, for example.
  • the working fluid is carbon-dioxide refrigerant.
  • the working fluid is however not restricted to carbon-dioxide refrigerant.
  • the working fluid is discharged from the compressing mechanism 8 in a supercritical state, and thus, at very high pressure.
  • the inner side of the hermetic container 2 can therefore be subjected to very high pressure, and thus, normally, the hermetic container 2 cannot avoid having a great thickness and weight for safety's sake.
  • the hermetic container 2 and compressor 1 structured as described above, which allow effective reduction of weight and size, are therefore favorable.
  • the present embodiment is a positive-displacement compressor 1
  • the present invention is applicable to hermetic fluid machines in general, including scroll compressors and expanders.
  • fluid machines to which the present invention is applied can be used to constitute a refrigeration cycle circuit incorporated in apparatuses other than vending machines.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP11734531A 2010-01-25 2011-01-24 Machine hydraulique Withdrawn EP2530322A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010013088A JP2011149393A (ja) 2010-01-25 2010-01-25 流体機械
PCT/JP2011/000366 WO2011089924A1 (fr) 2010-01-25 2011-01-24 Machine hydraulique

Publications (1)

Publication Number Publication Date
EP2530322A1 true EP2530322A1 (fr) 2012-12-05

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Application Number Title Priority Date Filing Date
EP11734531A Withdrawn EP2530322A1 (fr) 2010-01-25 2011-01-24 Machine hydraulique

Country Status (9)

Country Link
US (1) US20120294736A1 (fr)
EP (1) EP2530322A1 (fr)
JP (1) JP2011149393A (fr)
KR (1) KR20120093440A (fr)
CN (1) CN102834615A (fr)
CA (1) CA2787308A1 (fr)
IN (1) IN2012DN06559A (fr)
MX (1) MX2012008618A (fr)
WO (1) WO2011089924A1 (fr)

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Publication number Priority date Publication date Assignee Title
US10458438B2 (en) 2014-09-19 2019-10-29 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor

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MX2012008618A (es) 2012-10-05
US20120294736A1 (en) 2012-11-22
CA2787308A1 (fr) 2011-07-28
IN2012DN06559A (fr) 2015-10-23
JP2011149393A (ja) 2011-08-04
KR20120093440A (ko) 2012-08-22
CN102834615A (zh) 2012-12-19
WO2011089924A1 (fr) 2011-07-28

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