WO2011093086A1 - Machines a fluide - Google Patents

Machines a fluide Download PDF

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Publication number
WO2011093086A1
WO2011093086A1 PCT/JP2011/000459 JP2011000459W WO2011093086A1 WO 2011093086 A1 WO2011093086 A1 WO 2011093086A1 JP 2011000459 W JP2011000459 W JP 2011000459W WO 2011093086 A1 WO2011093086 A1 WO 2011093086A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
lubricating oil
fluid machine
sealed container
shielding
Prior art date
Application number
PCT/JP2011/000459
Other languages
English (en)
Japanese (ja)
Inventor
憲幸 小林
Original Assignee
サンデン株式会社
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 サンデン株式会社 filed Critical サンデン株式会社
Priority to US13/576,146 priority Critical patent/US20120308410A1/en
Priority to CN2011800074442A priority patent/CN102725527A/zh
Priority to BR112012018673A priority patent/BR112012018673A2/pt
Priority to MX2012008748A priority patent/MX2012008748A/es
Priority to EP11736801.9A priority patent/EP2514972A4/fr
Priority to CA2787527A priority patent/CA2787527A1/fr
Publication of WO2011093086A1 publication Critical patent/WO2011093086A1/fr

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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
    • F04B39/02—Lubrication
    • 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
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • 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
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • F04B39/0253—Hermetic compressors with oil distribution channels in the rotating shaft using centrifugal force for transporting the oil
    • 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
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F04C2210/261—Carbon dioxide (CO2)
    • 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
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/809—Lubricant sump

Definitions

  • the present invention relates to a fluid machine, and more particularly to a fluid machine suitable for a hermetic reciprocating compressor that compresses a carbon dioxide refrigerant.
  • This type of fluid machine includes an airtight container, an electric compression element that is housed in the airtight container and includes a compression element (driven unit) and an electric element (drive unit), and an oil reservoir provided in the compression element.
  • a hermetic compressor including a suction pipe having one end connected to a compression element and the other end opened near a lubricating oil reservoir (see, for example, Patent Document 1).
  • the crankshaft (rotary shaft) constituting the compression element is immersed in the lubricating oil stored in the inner bottom portion of the hermetic container and driven by the electric element so as to be provided in the crankshaft.
  • Lubricating oil is sucked up by the mechanism and lubricated to the sliding portion of the compression element.
  • the oil supply mechanism is rotationally driven by the electric element, the lubricating oil in the oil reservoir is scattered in a parabolic shape in the sealed container by the rotation of the oil supply mechanism when sucked up. Further, the lubricating oil is discharged from the rotating crankshaft into the sealed container, and the discharged lubricating oil scatters in a parabolic shape in the sealed container.
  • the lubricating oil thus scattered in the sealed container adheres to the inner wall of the sealed container and flows so as to circulate in the circumferential direction of the sealed container along the inner wall.
  • the time required for the lubricating oil to scatter and flow down to the oil reservoir and be stored becomes longer as the initial velocity at which the lubricating oil is scattered is larger and the viscosity force of the lubricating oil is larger.
  • the crankshaft and thus the oil pipe may rotate at about 3000 rpm, so the initial speed at which the lubricating oil is scattered increases in this case.
  • a hermetic compressor particularly a hermetic compressor using a carbon dioxide refrigerant as the working fluid
  • refrigeration oil having a higher viscous force than conventional products is often used. Tend to be longer.
  • the compressor is small and the maximum amount of lubricating oil stored in the oil reservoir is a small amount of about 200 cc, for example, if the required time is long, the amount of lubricating oil stored in the oil reservoir is reduced. It may decrease temporarily temporarily, and in the worst case, the amount of oil stored in the oil sump may temporarily become zero.
  • the present invention has been made based on the above-described circumstances, and an object of the present invention is to provide a fluid machine that can improve lubrication performance and improve reliability.
  • a fluid machine of the present invention is a fluid machine in which a drive unit and a driven unit to which the driving force of the drive unit is transmitted via a rotating shaft are accommodated in an airtight container. And an oil reservoir for storing the lubricating oil in the inner bottom portion of the sealed container, and an oil supply for supplying the lubricating oil in the oil reservoir to each sliding portion of the drive unit and the driven unit by rotating integrally with the rotating shaft.
  • the airtight container has a shielding portion that shields the flow of the lubricating oil in the circumferential direction on the inner side wall (Claim 1).
  • the shielding portion projects from the inner wall toward the oil sump portion (claim 2). Further, a frame that supports the drive unit and the driven unit is provided, and the frame is fixed to the shielding portion. Further, the sealed container is configured to include a bottom shell to be forged, the shielding portion is collectively formed when the bottom shell is forged (Claim 4), and the oil sump is formed when the bottom shell is forged. It is molded in a lump (claim 5).
  • the shielding part has a wave shape continuously bulging toward the oil sump part (Claim 6), and a plurality of shielding parts are provided (Claim 7). Furthermore, the pressure of the working fluid sucked into the driven unit and discharged from the driven unit acts in the sealed container, and the working fluid is a carbon dioxide refrigerant.
  • the lubricating oil scattered in the sealed container directly collides with the shielding part or directly collides with the shielding part. Even if it does not, it is greatly decelerated by exceeding the shielding part when it begins to circulate along the inner wall after adhering to the inner wall. The decelerated lubricating oil immediately flows down to the oil reservoir without continuing to circulate along the inner wall, greatly increasing the time required for the lubricating oil to flow down to the oil reservoir and be stored. Can be shortened.
  • the viscosity of the lubricating oil is large, and the maximum amount of oil stored in the oil reservoir is small, the circulation efficiency of the lubricating oil can be increased, and the lubrication of the fluid machine The performance can be improved.
  • a shielding part can be utilized as a base part for fixing a flame
  • the frame can be fixed to the sealed container without any problems, and the productivity of the fluid machine can be improved.
  • the shielding portion can be easily formed without requiring a separate member or a separate process by forming the shielding portion all together at the time of forging the bottom shell. The productivity of the machine can be improved.
  • the oil sump portion can be formed easily at the time of the forging molding of the bottom shell, so that the oil sump portion can be easily formed without requiring a separate member or separate processing.
  • the productivity of the fluid machine can be improved.
  • the shielding portion has a wave shape that continuously bulges toward the oil sump portion side, so that the scattered lubricating oil has one bulging of the shielding portion. Compared to the case, the probability of directly colliding with the shielding part is increased, or even when not directly colliding with the shielding part, it exceeds the shielding part when attached to the inner side wall and starts to circulate along the inner side wall. The number of times increases.
  • the lubricating oil can be decelerated more effectively, and the time required for the lubricating oil to flow down to the oil sump and be stored can be further shortened. Even when the viscosity of the lubricating oil is large and the maximum amount of oil stored in the oil reservoir is small, the circulation efficiency of the lubricating oil can be further increased and the lubricating performance of the fluid machine can be further improved. Can do.
  • the scattered lubricating oil has a higher probability of directly colliding with the shielding portion than when there is one shielding portion, Or even if it does not directly collide with the shielding part, the number of times exceeding the shielding part increases when it starts to circulate along the inner wall after adhering to the inner wall. Therefore, the lubricating oil can be decelerated more effectively, and the time required for the lubricating oil to flow down to the oil sump and be stored can be further shortened. Even when the viscosity of the lubricating oil is large and the maximum amount of oil stored in the oil reservoir is small, the circulation efficiency of the lubricating oil can be further increased and the lubricating performance of the fluid machine can be further improved. Can do.
  • the pressure of the working fluid discharged from the driven unit is increased to a supercritical state, and the temperature inside the fluid machine is high.
  • the temperature inside the fluid machine is low, the viscosity of the lubricating oil is large, and thus the scattered lubricating oil tends to hardly return.
  • the lubricating oil circulation efficiency can be increased and the lubrication performance of the fluid machine can be improved. It is preferable.
  • FIG. 5 is a plan view showing a lubricating oil flow path in the bottom shell of FIG. 4 from above.
  • the compressor 1 is a hermetic reciprocating compressor, and is categorized in detail as a positive displacement compressor called a reciprocating compressor or a piston compressor.
  • a configuration of a refrigeration cycle (not shown) incorporated in a vending machine. Used as equipment.
  • the refrigeration cycle includes a path through which a refrigerant as a working fluid of the compressor 1 circulates.
  • a carbon dioxide refrigerant that is a non-flammable natural refrigerant is used as the refrigerant.
  • the compressor 1 includes an airtight container 2, and an electric motor (drive unit) 4 and a compression mechanism (driven unit) to which the driving force of the electric motor 4 is transmitted are enclosed in the airtight container 2. 6) is housed.
  • the electric motor 4 includes a stator 8 that generates a magnetic field by power feeding and a rotor 10 that rotates by the magnetic field generated by the stator 8.
  • the rotor 10 is disposed coaxially inside the stator 8, and will be described later.
  • the main shaft portion 24 is fixed by shrinkage fitting. Electric power is supplied to the stator 8 from the outside of the compressor 1 through an electrical component 12 fixed to the sealed container 2 and a lead wire (not shown).
  • the compression mechanism 6 includes a crankshaft 14, a cylinder block 16, a piston 18, a connecting rod 20, and the like.
  • the crankshaft 14 includes an eccentric shaft portion 22 and a main shaft portion 24.
  • a cylinder bore 26 is formed integrally with the cylinder block 16, and a cylinder gasket 28, a later-described suction valve 50, and a valve plate 30 are sequentially arranged from the cylinder block 16 side so as to close the opening of the cylinder bore 26.
  • the head gasket 32 and the cylinder head 34 are pressed and fixed by bolts.
  • the stator 8 is bolted to the cylinder block 16 via a frame 36, and the frame 36 is fixed to the sealed container 2.
  • the electric motor 4 and the compression mechanism 6 are supported by a pedestal portion 38 below the frame 36, and the frame 36 is fixed to the sealed container 2 by the pedestal portion 38.
  • the bearing 42 of the main shaft portion 24 is disposed on the inner peripheral surface 40a, and the thrust trace (bearing) that receives the thrust load of the rotor 10 on the upper end surface 40b of the cylindrical portion 40.
  • a bearing 44 such as a thrust washer is disposed.
  • the valve plate 30 includes a refrigerant suction hole 46 and a discharge hole 48, both of which are opened and closed by a suction valve 50 and a discharge valve 52, which are reed valves, respectively.
  • the cylinder head 34 includes a refrigerant suction chamber 54 and a discharge chamber 56.
  • the discharge valve 52 When the discharge valve 52 is opened in the compression stroke of the piston 18, the discharge chamber 56 communicates with the cylinder bore 26 through the discharge hole 48.
  • the intake valve 50 is opened during the intake stroke of the piston 18, the intake chamber 54 communicates with the cylinder bore 26 via the intake hole 46.
  • a suction pipe 58 and a discharge pipe 60 are fixed to the sealed container 2, and one ends of the suction and discharge pipes 58 and 60 are connected to a suction chamber 54 and a discharge chamber 56 of the cylinder head 34, respectively.
  • the other ends of the suction and discharge pipes 58 and 60 are connected to a refrigeration cycle via a suction muffler and a discharge muffler (not shown), and these mufflers reduce the pulsation and noise of the refrigerant flowing between the compressor 1 and the refrigeration cycle. ing.
  • the connecting rod 20 is provided with a large end 62 to which the eccentric shaft portion 22 of the crankshaft 14 is rotatably connected at one end, and a small end 64 to which the piston 18 is reciprocally connected at the other end. It has been.
  • the small end portion 64 is connected to the piston 18 by a piston pin 66, and the piston pin 66 is secured to the piston 18 by a fixing pin 68.
  • the connecting rod 20 swings in conjunction with the eccentric rotation of the eccentric shaft portion 22 with the piston pin 66 as a fulcrum, and the piston 18 interlocks with the swinging motion of the connecting rod 20. It reciprocates in the cylinder bore 26.
  • the suction pressure of the refrigerant mainly acts in the sealed container 2, and a small amount of lubricating oil for lubricating the sliding portions of the electric motor 4 and the compression mechanism 6 such as the bearings 42 and 44 is present in the inner bottom portion 2 a of the sealed container 2.
  • an oil passage (oil supply mechanism) 70 is drilled from the substantially axial position of the lower end surface 22 a of the eccentric shaft portion 22 to the middle of the main shaft portion 24.
  • An upper portion of the oil passage 70 is opened from the outer peripheral surface 24 a of the main shaft portion 24, and an oil pipe (oil supply mechanism) 72 is connected to the lower portion of the oil passage 70.
  • the oil pipe 72 has an inclined portion 74 which is inclined from the substantially axial center of the eccentric shaft portion 22 toward the axial center of the main shaft portion 24 on the distal end side. It extends to the oil reservoir 76 having a concave shape in sectional view formed in the inner bottom 2a.
  • the oil sump portion 76 is formed to have a size and depth that allow a small amount of lubricating oil, for example, about 200 cc, to be stored so that the oil level is higher than the tip position of the oil pipe 74.
  • a centrifugal force acts on the lubricating oil in the inclined portion 74 in the oil pipe 72 in an obliquely upward outward direction. Is pumped from the oil reservoir 76 to the oil passage 74. Further, along with the eccentric rotation of the oil pipe 72, a part of the lubricating oil in the oil reservoir 76 is scattered in a parabolic shape in the sealed container 2.
  • the operation and action of the compressor 1 will be described.
  • the rotor 10 fixed to the main shaft portion 24 is rotated by supplying power to the stator 8, and consequently the crankshaft 14 is rotated, and the piston 18 reciprocates in the cylinder bore 26 via the connecting rod 20.
  • the reciprocating motion of the piston 18 causes the refrigerant to be sucked into the cylinder bore 26 from the refrigeration cycle, and the refrigerant is compressed by the cylinder bore 26 and further discharged to the refrigeration cycle.
  • the piston 18 operates in the direction of decreasing the volume of the cylinder bore 26 and the refrigerant in the cylinder bore 26 is compressed and the pressure in the cylinder bore 26 exceeds the discharge pressure of the refrigerant, the pressure in the cylinder bore 26 and the discharge chamber 56 are increased.
  • the discharge valve 52 opens due to the difference from the internal pressure. The compressed refrigerant is guided to the discharge chamber 56 via the discharge hole 48 and discharged to the refrigeration cycle via the discharge pipe 60.
  • the pressure in the cylinder bore 26 decreases.
  • the discharge valve 52 closes according to the difference between the pressure in the cylinder bore 26 and the pressure in the discharge chamber 56.
  • the suction valve 50 opens according to the difference between the pressure in the cylinder bore 26 and the pressure in the suction chamber 54. The refrigerant in the refrigeration cycle is guided to the suction chamber 54 through the suction pipe 58 and is sucked into the cylinder bore 26 through the suction hole 46.
  • the scattered lubricating oil flows down to the eccentric shaft portion 22 side and lubricates the vicinity of the large end portion 62. Further, the lubricating oil is scattered toward the piston 18 by the flange portion 22b formed on the eccentric shaft portion 22, and lubricates the vicinity of the skirt portion 18a of the piston 18.
  • a part of the lubricating oil flowing out from the oil passage 70 rises along an outer peripheral groove (not shown) formed in the crankshaft 14 by centrifugal force, and forms an oil film between the crankshaft 14 and the frame 36. Then, the bearing 42 is lubricated and moved to the upper end side of the crankshaft 14. The lubricating oil reaches the upper end surface 40b of the cylindrical portion 40 and lubricates the bearing 44, and then flows down to the oil sump portion 76 by gravity.
  • the lubricating oil that cannot pass through the bearing 44 rises as it is up the inner wall surface 10a of the rotor 10 to the upper end of the rotor 10, is scattered by the centrifugal force due to the rotation of the rotor 10, cools the stator 8, and then To flow down to the oil sump 76.
  • the sealed container 2 is composed of two shells, a top shell 78 covering the electric motor 4 side and a bottom shell 80 covering the compression mechanism 6 side. It has a structure. Since the crankshaft 14 and the connecting rod 20 are positioned so as to be substantially orthogonal within the sealed container 2, the longitudinal direction of the electric motor 4 is accommodated in the depth direction of the top shell 78, and the top shell 78 is the bottom shell 80. Compared to, it has a deep bottom shape. On the other hand, the compression mechanism 6 is accommodated in the radial direction of the bottom shell 80 in the longitudinal direction, and the bottom shell 80 has a shallow bottom shape as compared with the top shell 78.
  • Each of the shells 78 and 80 has root edges protruding from the respective open end portions 78a and 80a, and the groove portions 82 are formed by abutting each root edge with each other.
  • Each of the shells 78 and 80 is joined by forming a bead-shaped welded portion 84 continuous around the entire circumference of the groove portion 82 by a single welding operation, that is, a single butt formed by a single welding operation. Joined with welded joints.
  • the bottom shell 80 is formed by forging, and has a gripping portion 86 that is gripped during the forging molding.
  • the gripping portion 86 protrudes from the outer top portion 80c of the bottom shell 80 at the radial center side with respect to the side portion 80b of the bottom shell 80. Is done.
  • the oil sump portion 76 is recessed at the position of the inner bottom portion 2a on the back side of the gripping portion 86 so as to be substantially similar to the outer shape of the gripping portion 86. That is, the bottom shell 80 is formed from the side portion 80b to the outer top portion 80c with substantially the same thickness as the side portion 80b.
  • a base plate 88 for stably mounting the compressor 1 is attached around the gripping portion 86 of the outer top portion 80c.
  • anti-vibration rubber (not shown) to the lower surface of the base plate 88, the compressor 1 can be fixed while suppressing vibration during operation.
  • the inner wall 80 d near the opening end 80 a of the bottom shell 80 swells toward the radial center of the bottom shell 80, that is, toward the oil reservoir 76.
  • a shielding portion 90 for the lubricating oil that has been discharged is formed.
  • the shielding portion 90 has a wave shape that is continuously bulged twice toward the oil sump portion 76 side, and two shield portions 90 are provided facing the position where the oil sump portion 76 is sandwiched between the bottom shell 80 as viewed from above. It has been.
  • a frame 36 that supports the stator 8 and the cylinder block 16 shown in FIG. 1 is fixed to the upper surface 90 a of the shielding portion 90.
  • the shielding portion 90 also has a function as a pedestal portion for fixing the frame 36 to the sealed container 2. is doing.
  • the gripping portion 86, the oil sump portion 76, and the shielding portion 90 formed on the bottom shell 80 are all formed at the same time when the bottom shell 80 is forged.
  • the lubricating oil tends to flow so as to circulate in the circumferential direction of the bottom shell 80 along the inner wall 80d.
  • the required time T becomes longer as the initial velocity v at which the lubricating oil is scattered is larger and the viscous force of the lubricating oil is larger.
  • the compressor 1 is small and the maximum oil storage amount of the oil reservoir 76 is a small amount of about 200 cc as described above, if the required time T is long, the oil storage amount of the oil reservoir 76 is reduced.
  • the oil supply mechanism may be reduced to a temporary state and may be zero in the worst case, and the oil supply mechanism will not function as an idle operation, so that each sliding part of the electric motor 4 and the compression mechanism 6 is appropriately supplied with oil. This causes a problem that the lubrication performance of the compressor 1 is remarkably deteriorated.
  • the lubricating oil circulation efficiency is high.
  • the lubricating performance of the compressor 1 can be improved.
  • the shielding portion 90 can be used as a pedestal portion for fixing the frame 36 to the sealed container 2, so that the frame can be used without requiring a separate part or member. 36 can be fixed to the airtight container 2, and the productivity of the compressor 1 can be improved.
  • the shielding portion 90 and the oil sump portion 76 are formed at the same time when the bottom shell 80 is forged, thereby easily forming the shielding portion 90 and the oil sump portion 76 without requiring separate members or processing. And the productivity of the compressor 1 can be improved. Furthermore, the shielding portion 90 has a wave shape that is continuously swollen twice toward the oil sump portion 76 side. Further, by providing two shielding portions 90, the scattered lubricating oil Compared to the case where there is only one bulge and the case where there is only one shielding part 90, the probability of directly colliding with the shielding part 90 is increased, or directly to the shielding part 90.
  • the lubricating oil can be decelerated more effectively, and the required time T from when the lubricating oil is scattered until it flows down to the oil reservoir 76 and stored can be further shortened. Is operated at high speed, the viscosity of the lubricating oil is large, and even when the maximum oil storage amount of the oil reservoir 76 is small, the circulation efficiency of the lubricating oil can be further increased, and the lubricating performance of the compressor 1 can be improved. Can be further improved.
  • the shielding portion is not limited to a shape that protrudes toward the oil reservoir 76 on the inner wall 80d as in the shielding portion 90 of the present embodiment, and the circumferential portion of the inner wall 80d is not limited.
  • Various shapes and installation numbers are conceivable as long as the lubricating oil can be decelerated by blocking the smooth flow of the lubricating oil and guided to the oil reservoir 76.
  • a thing like a shielding plate may be provided on the inner wall 80d, or a part of the inner wall 80d may be recessed in a wave shape.
  • jagged irregularities may be provided in the circumferential direction of the inner wall 80d, or stepped irregularities may be provided in the circumferential direction of the inner wall 80d.
  • the working fluid of the compressor 1 of the present embodiment is a carbon dioxide refrigerant, it is not limited to this.
  • the working fluid is carbon dioxide refrigerant
  • the pressure of the working fluid discharged from the compression mechanism 6 becomes high to the supercritical state, and the temperature inside the compressor 1 becomes high, so that the viscosity is relatively high.
  • Lubricating oil is used to prevent oil film breakage due to low viscosity at high temperatures.
  • the temperature inside the compressor 1 is low, the viscosity of the lubricating oil is high, and therefore the scattered lubricating oil tends to be difficult to return.
  • the lubricating oil circulation efficiency can be increased and the lubricating performance of the compressor 1 can be improved even if the lubricating oil has a large viscosity and the scattered lubricating oil tends to hardly return. This is preferable.
  • the present Example demonstrates the positive displacement compressor 1, this invention is applicable to general sealed fluid machines, such as a scroll compressor and an expander, These fluid machines are other than a vending machine. Of course, it can be used as a component device of the refrigeration cycle incorporated in the.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne des machines à fluide à performance de lubrification et à fiabilité améliorées. Une machine à fluide (1) comprend une unité d'entraînement (4) et une unité entraînée (6) à laquelle la force d'entraînement de l'unité d'entraînement est transmise via un arbre rotatif (14), toutes deux étant hébergées dans un contenant étanche (2). La machine à fluide comprend également: un réservoir d'huile (76) stockant un lubrifiant disposé sur la surface inférieure interne (2a) du contenant étanche ; et des mécanismes de lubrification (70, 72) fournissant le lubrifiant du réservoir d'huile aux parties coulissantes de l'unité d'entraînement et de l'unité entraînée par rotation, de manière solidaire avec l'arbre rotatif. Le contenant étanche comprend une partie de blocage (90) placée sur sa paroi latérale intérieure (80d) qui bloque l'écoulement du lubrifiant dans la direction périphérique sur ladite paroi latérale intérieure.
PCT/JP2011/000459 2010-01-29 2011-01-27 Machines a fluide WO2011093086A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US13/576,146 US20120308410A1 (en) 2010-01-29 2011-01-27 Fluid Machine
CN2011800074442A CN102725527A (zh) 2010-01-29 2011-01-27 流体机械
BR112012018673A BR112012018673A2 (pt) 2010-01-29 2011-01-27 máquina de fluido
MX2012008748A MX2012008748A (es) 2010-01-29 2011-01-27 Maquina de fluido.
EP11736801.9A EP2514972A4 (fr) 2010-01-29 2011-01-27 Machines a fluide
CA2787527A CA2787527A1 (fr) 2010-01-29 2011-01-27 Machines a fluide

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010-018425 2010-01-29
JP2010018425A JP2011157831A (ja) 2010-01-29 2010-01-29 流体機械

Publications (1)

Publication Number Publication Date
WO2011093086A1 true WO2011093086A1 (fr) 2011-08-04

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PCT/JP2011/000459 WO2011093086A1 (fr) 2010-01-29 2011-01-27 Machines a fluide

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US (1) US20120308410A1 (fr)
EP (1) EP2514972A4 (fr)
JP (1) JP2011157831A (fr)
KR (1) KR20120103744A (fr)
CN (1) CN102725527A (fr)
BR (1) BR112012018673A2 (fr)
CA (1) CA2787527A1 (fr)
MX (1) MX2012008748A (fr)
WO (1) WO2011093086A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3421804B1 (fr) * 2017-06-26 2021-04-21 BSH Hausgeräte GmbH Sèche-linge comportant une pompe à chaleur
CN109296540A (zh) * 2018-09-25 2019-02-01 珠海凌达压缩机有限公司 液位调节装置、压缩机壳体及压缩机

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JPS62129595A (ja) * 1985-11-29 1987-06-11 Hitachi Ltd 密閉形スクロ−ル圧縮機
JPS62197675A (ja) * 1986-02-25 1987-09-01 Matsushita Refrig Co 冷媒圧縮機
JPS62258182A (ja) * 1986-05-02 1987-11-10 Hitachi Ltd 密閉形スクロ−ル圧縮機
JPH0211888A (ja) * 1988-06-29 1990-01-16 Matsushita Electric Ind Co Ltd 密閉型スクロール圧縮機
JPH06294380A (ja) 1993-04-12 1994-10-21 Matsushita Refrig Co Ltd 密閉型圧縮機
JP2000073951A (ja) * 1998-08-31 2000-03-07 Mitsubishi Electric Corp 冷媒圧縮機及びこの冷媒圧縮機を用いた冷凍サイクル
JP2004308623A (ja) * 2003-04-10 2004-11-04 Matsushita Electric Ind Co Ltd 密閉型圧縮機

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KR100422367B1 (ko) * 2001-07-14 2004-03-12 삼성광주전자 주식회사 밀폐형 압축기의 오일 픽업장치
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JPS62129595A (ja) * 1985-11-29 1987-06-11 Hitachi Ltd 密閉形スクロ−ル圧縮機
JPS62197675A (ja) * 1986-02-25 1987-09-01 Matsushita Refrig Co 冷媒圧縮機
JPS62258182A (ja) * 1986-05-02 1987-11-10 Hitachi Ltd 密閉形スクロ−ル圧縮機
JPH0211888A (ja) * 1988-06-29 1990-01-16 Matsushita Electric Ind Co Ltd 密閉型スクロール圧縮機
JPH06294380A (ja) 1993-04-12 1994-10-21 Matsushita Refrig Co Ltd 密閉型圧縮機
JP2000073951A (ja) * 1998-08-31 2000-03-07 Mitsubishi Electric Corp 冷媒圧縮機及びこの冷媒圧縮機を用いた冷凍サイクル
JP2004308623A (ja) * 2003-04-10 2004-11-04 Matsushita Electric Ind Co Ltd 密閉型圧縮機

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Title
See also references of EP2514972A4

Also Published As

Publication number Publication date
CN102725527A (zh) 2012-10-10
JP2011157831A (ja) 2011-08-18
BR112012018673A2 (pt) 2016-05-03
CA2787527A1 (fr) 2011-08-04
MX2012008748A (es) 2012-11-23
EP2514972A1 (fr) 2012-10-24
KR20120103744A (ko) 2012-09-19
US20120308410A1 (en) 2012-12-06
EP2514972A4 (fr) 2014-02-26

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