WO2007111194A1 - 圧縮機 - Google Patents
圧縮機 Download PDFInfo
- Publication number
- WO2007111194A1 WO2007111194A1 PCT/JP2007/055631 JP2007055631W WO2007111194A1 WO 2007111194 A1 WO2007111194 A1 WO 2007111194A1 JP 2007055631 W JP2007055631 W JP 2007055631W WO 2007111194 A1 WO2007111194 A1 WO 2007111194A1
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- WO
- WIPO (PCT)
- Prior art keywords
- oil
- passage
- lid
- chamber
- compressor according
- Prior art date
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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
- F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
-
- 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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/109—Lubrication
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- 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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
-
- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
- F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
-
- 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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1863—Controlled by crankcase pressure with an auxiliary valve, controlled by
- F04B2027/1872—Discharge pressure
Definitions
- the present invention relates to, for example, a compressor that separates oil contained in discharge gas and returns the separated oil to a low pressure region.
- Patent Document 1 discloses a compressor having an oil storage chamber.
- An oil separation chamber is formed in the rear housing of the compressor so as to extend in the radial direction of the rear housing, and an oil storage chamber is provided at the rear end portion of the rear housing. It is provided so as to protrude.
- the rear housing is formed with a through hole that allows the oil separation chamber and the oil storage chamber to communicate with each other.
- the rear housing is provided with a discharge chamber through which compressed refrigerant gas containing mist-like oil is discharged, and an inflow passage that connects the discharge chamber and the oil separation chamber is formed.
- a discharge hole is connected to the oil separation chamber, and a check valve unit for preventing a reverse flow of the refrigerant gas from the oil separation chamber to the discharge chamber is attached to the discharge hole.
- the check valve unit includes a pipe portion protruding into the oil separation chamber, and the pipe portion and the oil separation chamber constitute oil separation means.
- the rear housing is formed with a gas return passage for communicating the annular port of the pedestal portion provided in the check valve unit and the oil storage chamber.
- the gas return passage has a smaller diameter (about 1 mm) than the through hole, and functions as a passage for returning the refrigerant gas that has entered the oil storage chamber to the discharge passage including the annular port.
- the compressed refrigerant gas in the discharge chamber flows into the oil separation chamber through the inflow passage.
- the refrigerant gas that has flowed into the oil separation chamber collides with the outer peripheral surface of the pipe portion and swirls around the outer peripheral surface, so that the mist oil contained in the refrigerant gas is separated from the refrigerant gas cartridge.
- the separated oil is stored at the bottom of the oil separation chamber and flows into the oil storage chamber through the inlet of the through hole.
- the oil in the oil storage chamber is returned to the crank chamber or the like through the oil return passage.
- the refrigerant gas from which the oil has been separated passes through the pipe section and check valve, and passes through the discharge pipe to the external refrigerant. Supplied to the circuit. Since a gas return passage is formed between the refrigerant gas discharge path and the oil storage chamber, the refrigerant gas flows due to the differential pressure ⁇ P between the oil separation chamber and the discharge path.
- the oil, whose refrigerant gas power is also separated in the oil separation chamber rides on this flow and immediately flows into the oil storage chamber through the through hole.
- Patent Document 2 discloses a swash plate type compressor having an oil separation chamber.
- a protrusion is provided at the top of the rear cylinder block of the compressor, and a cyclone type oil separation chamber is formed inside the protrusion.
- the compressor has a through hole adjacent to the oil separation chamber, and the through hole communicates with a muffler chamber formed in the rear cylinder block.
- a primary oil reservoir for collecting separated oil is formed below the oil separation chamber.
- a main oil reservoir is provided on the side of the oil separation chamber and the primary oil reservoir.
- the valve seat surface at the bottom of the main oil reservoir has an opening for a return oil hole communicating with the swash plate chamber, which is a low pressure region.
- the return oil hole opening is equipped with a reed valve that also has panel steel plate force, and the reed valve can be deformed according to the differential pressure between the high pressure region and the low pressure region to control the flow rate of oil flowing through the return oil hole It is.
- the high-pressure compressed refrigerant gas that has flowed into the muffler chamber is introduced into the oil separation chamber through the through hole.
- the refrigerant gas introduced into the oil separation chamber swirls along the peripheral wall of the oil separation chamber, and mist-like oil contained in the refrigerant gas is separated from the refrigerant gas by the action of centrifugal force.
- the separated oil is collected in the primary oil sump chamber, and is stored in the main oil sump chamber via a through hole due to a differential pressure between the high pressure region and the low pressure region.
- the opening of the reed valve is controlled in accordance with the differential pressure between the high pressure region and the low pressure region. For example, when the differential pressure is small, the opening of the reed valve increases and the main oil reservoir chamber force return oil hole is The amount of oil that flows back to the swash plate chamber increases. When the differential pressure is large, the opening of the reed valve is small, and the amount of oil returned to the swash plate chamber via the main oil reservoir chamber return oil hole is small.
- both the compressors of Patent Document 1 and Patent Document 2 have a problem that the degree of freedom of arrangement of the oil separator and the storage chamber of the separated oil is low.
- Patent Document 1 Japanese Patent Application Laid-Open No. 2004-218610
- Patent Document 2 JP-A-5-240158
- An object of the present invention is to provide a compressor that can be reduced in size.
- a compressor for compressing refrigerant gas containing oil includes a discharge chamber, a discharge passage, a lid, an oil separator, an introduction passage, an oil reservoir, an oil storage chamber, and an oil passage.
- a compressed refrigerant gas is discharged into the discharge chamber.
- the discharge passage is formed in the discharge chamber.
- the lid is provided in the discharge passage and partitions the discharge passage from the discharge chamber.
- the oil separator is provided in the discharge passage, and a separation chamber is formed between the oil separator and the lid. The oil separator separates the oil from the refrigerant gas introduced into the separation chamber.
- the introduction passage introduces the refrigerant gas from the discharge chamber into the separation chamber.
- the oil reservoir is provided around the lid and stores oil separated from the refrigerant gas tank.
- the oil storage chamber stores the separated oil and communicates with a low pressure region in the compressor having a pressure lower than the pressure of the discharge chamber.
- Above The oil passage allows the oil reservoir to communicate with the oil storage chamber.
- FIG. 1 is a cross-sectional view of a compressor according to a first embodiment of the present invention.
- FIG. 2 is an enlarged cross-sectional view of the main part of the compressor shown in FIG.
- FIG. 3 is a schematic cross-sectional view taken along line 3-3 in FIG.
- FIG. 4 is an enlarged cross-sectional view of a main part of a compressor according to a second embodiment of the present invention.
- FIG. 5 is an enlarged cross-sectional view of a main part of a compressor according to a third embodiment of the present invention.
- FIG. 6 is an enlarged cross-sectional view of a main part of a compressor according to a fourth embodiment of the present invention.
- FIG. 7 is an enlarged cross-sectional view of a main part of a compressor according to a fifth embodiment of the present invention.
- FIG. 8 is an enlarged cross-sectional view of a main part of a compressor according to a sixth embodiment of the present invention.
- FIG. 9 is an enlarged cross-sectional view of a main part of a compressor according to a seventh embodiment of the present invention.
- FIG. 10 is an enlarged cross-sectional view of a main part of a compressor according to an eighth embodiment of the present invention.
- FIG. 11 is an enlarged cross-sectional view of a main part of a compressor according to a ninth embodiment of the present invention.
- FIG. 12 is a perspective view of a lid according to a ninth embodiment of the present invention.
- FIG. 13 is an enlarged cross-sectional view of a main part of a compressor according to a tenth embodiment of the present invention.
- FIG. 14 is a perspective view of a lid according to an eleventh embodiment of the present invention.
- FIG. 15 (a) is a schematic cross-sectional view of a compressor according to a modification of the ninth to eleventh embodiments, and (b) is an enlarged cross-sectional view of a main part of a compressor according to another modification.
- FIG. 16 is an enlarged cross-sectional view of a main part of a compressor according to a first other example.
- FIG. 17 is an enlarged cross-sectional view of a main part of a compressor according to a second example.
- variable capacity swash plate compressor (hereinafter simply referred to as a compressor) according to a first embodiment will be described with reference to FIGS.
- the compressor housing is joined to the front nosing member 12 joined to the front end of the cylinder block 11 and to the rear end of the cylinder block 11 via a valve port forming body 13. And a rear housing member 14.
- a crank chamber 15 is defined in a region surrounded by the cylinder block 11 and the front housing member 12.
- a drive shaft 16 is rotatably disposed in the crank chamber 15. The drive shaft 16 is mounted on the vehicle. It is operatively connected to the engine 17 and is rotated by the power supply from the engine 17.
- a lug plate 18 is fixed on the drive shaft 16 so as to be rotatable integrally with the rotary shaft 16.
- a swash plate 19 is accommodated in the crank chamber 15.
- the swash plate 19 is supported by the drive shaft 16, can slide on the drive shaft 16 along the axis of the drive shaft 16, and can tilt with respect to the drive shaft 16.
- a hinge mechanism 20 is interposed between the lug plate 18 and the swash plate 19.
- the swash plate 19 can be rotated in synchronization with the lug plate 18 and the drive shaft 16 via the hinge mechanism 20 and can be tilted with the movement of the drive shaft 16 in the axial direction.
- the inclination angle of the swash plate 19 is controlled by a capacity control valve 21 described later.
- a plurality of cylinder bores 11a (only one is shown in FIG. 1) are formed in the cylinder block 11, and a single-headed piston 22 is accommodated in each cylinder bore 1 la so as to be reciprocally movable.
- Each piston 22 is moored to the outer periphery of the swash plate 19 via a bush 23. Accordingly, the rotational motion of the swash plate 19 accompanying the rotation of the drive shaft 16 is converted into the reciprocating linear motion of the piston 22 via the shoe 23.
- a compression chamber 24 surrounded by the piston 22 and the valve port forming body 13 is defined on the back side (right side in FIG. 1) of the cylinder bore 11a.
- a suction chamber 25 is defined in the rear housing member 14 and a discharge chamber 26 is defined around the suction chamber 25.
- the refrigerant gas in the suction chamber 25 passes through the suction port 27 and the suction valve 28 formed in the valve / port forming body 13 as the piston 22 moves from the top dead center position to the bottom dead center position. Inhaled into the compression chamber 24.
- the refrigerant gas sucked into the compression chamber 24 is compressed to a predetermined pressure by the piston 22 moving to the bottom dead center position force and the top dead center position, and is discharged to the discharge port 29 formed in the valve 'port formation 13. And it is discharged into the discharge chamber 26 through the discharge valve 30.
- an extraction passage 31 and an air supply passage 32 are provided in the housing.
- the extraction passage 31 is for leading the refrigerant gas from the crank chamber 15 to the suction chamber 25.
- the supply passage 32 is for introducing the refrigerant gas discharged from the discharge chamber 26 into the crank chamber 15.
- a capacity control valve 21 is provided in the middle of the air supply path 32.
- crank chamber 15 is provided via the air supply passage 32.
- the balance between the amount of introduced high-pressure refrigerant gas introduced and the amount of refrigerant gas derived from the crank chamber 15 via the extraction passage 31 is controlled to determine the pressure in the crank chamber 15.
- a cylindrical hole 33 is formed in the upper portion of the rear housing member 14 so as to communicate with the discharge chamber 26.
- the cylindrical hole 33 forms a discharge passage provided in the discharge chamber 26.
- the cylindrical hole 33 extends in parallel with the axis of the drive shaft 16.
- a cylindrical oil separator 35 is disposed at the axial center of the cylindrical hole 33.
- the oil separator 35 is fixed to the cylindrical hole 33 by directing the cylindrical part 35a forward and fitting a pedestal part 35b having a diameter larger than the cylindrical part 35a into the cylindrical hole 33.
- a check valve 36 is accommodated adjacent to the oil separator 35 on the back side (right side in FIG. 2) from the axial center of the cylindrical hole 33.
- the check valve 36 is for preventing the refrigerant from flowing back from the external refrigerant circuit 48 to the discharge chamber 26.
- An enlarged diameter hole 33a having a diameter larger than the diameter of the cylindrical hole 33 is formed at the inlet portion (left side in FIG. 2) of the cylindrical hole 33. Thereby, a step portion is formed on the inner wall surface 33b of the cylindrical hole 33.
- a lid 34 that partitions the discharge chamber 26 and the cylindrical hole 33 is attached to the inlet of the cylindrical hole 33.
- the lid 34 has a flange portion 34a and an outer ring portion 34b. On the outer peripheral surface of the lid 34, a step portion is formed by the flange portion 34a and the outer ring portion 34b.
- the lid 34 is fixed to the cylindrical hole 33 by fitting the outer ring part 34b to the inner wall surface 33b of the cylindrical hole 33 and fitting the flange part 34a to the enlarged diameter hole 33a.
- the thickness dimension e in the axial direction of the flange portion 34a is set to be smaller than the depth dimension in the axial direction of the diameter expansion hole 33a (ef).
- a separation chamber 42 is formed in a space surrounded by the lid 34, the oil separator 35, and the inner wall surface 33 b of the cylindrical hole 33.
- the discharge chamber 26 and the separation chamber 42 communicate with each other via an introduction passage 40, and the discharge refrigerant gas is introduced from the discharge chamber 26 to the separation chamber 42 through the introduction passage 40.
- the introduction passage 40 is configured so as to be substantially tangent to the cross-sectional circle of the inner wall surface 33b of the separation chamber 42 in the streamline force of the discharged refrigerant gas introduced into the separation chamber 42. ing. Accordingly, the discharged refrigerant gas introduced into the separation chamber 42 through the introduction passage 40 swirls clockwise along the inner wall surface 33b.
- the discharge refrigerant gas swirls along the inner wall surface 33b in the space between the inner wall surface 33b and the cylindrical portion 35a of the oil separator 35, so that the oil contained in the discharge refrigerant gas Is centrifuged from the discharged refrigerant gas.
- the discharged refrigerant gas from which the oil has been separated is introduced into the check valve 36 from the separation chamber 42 through the pipe 35c inside the oil separator 35, and discharged toward the discharge flange 43 through the discharge passage 41.
- the pipe 35c penetrates the oil separator 35 in the longitudinal direction, and opens to the separation chamber 42 at the position of the tip facing the lid 34. The separated oil is stored near the bottom of the lid 34 at the bottom of the separation chamber 42.
- annular space 37 is formed between the stepped portion on the outer peripheral surface of the lid 34 and the stepped portion on the inner wall surface 33b of the separation chamber 42.
- the annular space 37 is an annular groove having a square cross section formed around the lid 34.
- the annular space 37 functions as an oil reservoir that communicates with the separation chamber 42.
- a step 33c having a constant width is formed on the inner wall surface 33b of the separation chamber 42 which is located below the lid 34 and fits with the outer ring portion 34b of the lid 34, and the separation chamber is formed by the step 33c.
- a throttle passage 38 is formed for communicating 42 with the annular space 37. Therefore, the oil G separated from the discharged refrigerant gas and stored in the bottom portion of the separation chamber 42 flows toward the annular space 37 through the throttle passage 38.
- a discharge flange 43 is provided on the upper surface of the cylinder block 11 so as to protrude to the outside.
- a high-pressure fluid chamber 44 and a low-pressure fluid chamber 45 are formed inside the discharge flange 43, and a throttle portion 46 is provided between the fluid chambers 44 and 45.
- Below the low-pressure fluid chamber 45 is provided an oil storage chamber 47 for storing oil.
- the high pressure fluid chamber 44 communicates with the separation chamber 42 via the discharge passage 41, and the low pressure fluid chamber 45 communicates with the external refrigerant circuit 48 via a port (not shown). Therefore, the discharged refrigerant gas discharged from the separation chamber 42 is introduced into the high-pressure fluid chamber 44 through the discharge passage 41 and flows into the low-pressure fluid chamber 45 through the throttle portion 46.
- the oil storage chamber 47 and the annular space 37 communicate with each other via an oil passage 39. Therefore, the separation chamber 42 and the oil storage chamber 47 are connected via the throttle passage 38, the annular space 37, and the oil passage 39.
- the oil storage chamber 47 communicates with a crank chamber 15 and the like, which is a low pressure region, through an oil return passage (not shown).
- the discharged refrigerant gas is introduced into the separation chamber 42 through the introduction passage 40.
- the discharged refrigerant gas introduced into the separation chamber 42 flows in a direction toward the tip of the cylindrical portion 35a while swirling along the inner wall surface 33b in the space between the inner wall surface 33b and the cylindrical portion 35a of the oil separator 35.
- the mist-like oil contained in the discharged refrigerant gas is separated from the refrigerant gas by the action of centrifugal force.
- the separated oil swirls in the separation chamber 42 under the influence of the swirling refrigerant gas, but part of it falls down along the inner wall surface 33b of the separation chamber 42 due to its own weight, and the bottom of the separation chamber 42 Store near the bottom of the lid 34.
- the discharged refrigerant gas from which the oil has been separated is also introduced into the check valve 36 through the pipe 35c at the tip of the cylindrical portion 35a of the oil separator 35.
- the discharged refrigerant gas from which the oil has been separated is introduced into the check valve 36 and then discharged to the discharge flange 43 through the discharge passage 41. Then, the discharged refrigerant gas introduced into the high-pressure fluid chamber 44 of the discharge flange 43 flows into the low-pressure fluid chamber 45 and is supplied to the external refrigerant circuit 48 through the discharge port.
- the oil G stored in the bottom portion of the separation chamber 42 flows through the throttle passage 38 toward the annular space 37.
- the annular space 37 and the oil storage chamber 47 communicate with each other, and the oil storage chamber 47 communicates with the crank chamber 15 and the like, which is a low pressure region having a pressure lower than the pressure of the discharge chamber 26.
- a differential pressure ⁇ is generated between the separation chamber 42 and the oil storage chamber 47. That is, the pressure in the separation chamber 42 communicating with the discharge chamber 26 is larger than the pressure in the oil storage chamber 47. Due to the action of this differential pressure ⁇ , the oil that flows into the annular space 37 from the separation chamber 42 rises in the annular space 37, and the oil It flows into the oil storage chamber 47 through the passage 39.
- the oil stored in the oil storage chamber 47 is returned to the crank chamber 15 and the like through an oil return passage (not shown) and used for lubricating the sliding portion of the compressor.
- An oil separator 35 is disposed in a cylindrical hole (discharge passage) 33 in the discharge chamber 26, and the separation chamber 42 is formed by closing the inlet of the cylindrical hole 33 with a lid 34.
- An annular space 37 is formed around the lid 34, and a throttle passage 38 that connects the annular space 37 and the separation chamber 42 is provided.
- the oil G stored in the separation chamber 42 passes through the annular space 37 in the oil storage chamber 47 above the separation chamber 42 using the differential pressure ⁇ between the separation chamber 42 and the oil storage chamber 47. It can be made to flow away. Therefore, the annular space 37 and the passage diameter of the oil passage 39 that allows the annular space 37 and the oil storage chamber 47 to communicate with each other can be set freely. As a result, the degree of freedom of arrangement of the oil storage chamber 47 can be improved, and the compressor can be miniaturized.
- annular space 37 is formed by the steps provided on the outer peripheral surface of the lid 34 and the inner wall surface of the separation chamber 42, no special processing is required to form the annular space 37. Machining is easy and man-hours can be reduced.
- This embodiment is obtained by changing the form of the narrowing passage for communicating the separation chamber 42 and the annular space 37 in the first embodiment, and the other configurations are common. Therefore, here For convenience of explanation, a part of the reference numerals used in the previous explanation is used in common, the explanation of the common configuration is omitted, and only the changed part is explained.
- the throttle passage 51 in this embodiment has an outermost portion 34b of the outer ring 34b of the lid 34 extending in a direction perpendicular to the axis of the lid 34 (vertical direction in FIG. 4). It is formed by a through hole 52 provided in the lower part.
- the throttle chamber 51 allows the separation chamber 42 and the annular space 37 to communicate with each other. Therefore, the oil G separated from the discharged refrigerant gas and stored in the bottom portion of the separation chamber 42 flows through the throttle passage 51 toward the annular space 37.
- the throttle passage 51 for communicating the separation chamber 42 and the annular space 37 is formed. Since only the lid 34 that does not need to cover the housing of the compressor is formed to form the throttle passage 51, the force can be easily obtained.
- the compressor according to this embodiment is obtained by changing the forms of the lid 34 and the oil separator 35 in the first embodiment, and other configurations are common. Therefore, here, for convenience of explanation, a part of the reference numerals used in the previous explanation is used in common, the explanation of the common configuration is omitted, and only the changed part is explained.
- a lid 62 that partitions the separation chamber 42 and the discharge chamber 26 is formed integrally with the oil separator 35.
- the member 61 includes a lid 62 that partitions the separation chamber 42 and the discharge chamber 26, a cylindrical portion 63 that functions as an oil separator 35, and a pedestal portion 64 that holds the cylindrical portion 63.
- a pipe 65 is provided inside the member 61, and the pipe 65 opens rearward (to the right in FIG. 5).
- the pedestal 64 of the member 61 is inserted into the cylindrical hole 33 as shown in FIG. 5 with the check valve 36 attached to the opening side of the pipe 65.
- the member 61 becomes the cylindrical hole 33. It is fixed.
- the axial thickness dimension e of the flange portion 62a is set to be smaller than the axial dimension of the diameter expansion hole 33a (ef).
- a gas passage hole 63a that communicates the separation chamber 42 and the pipe 65 is formed so as to extend in a direction intersecting the central axis of the pipe 65, and opens to the separation chamber 42.
- the gas passage hole 63a extends in a direction perpendicular to the central axis of the pipe 65.
- a stepped portion is formed by the flange portion 62a and the outer ring portion 62b.
- an annular space 37 as an oil reservoir is formed between the stepped portion on the outer peripheral surface of the lid 62 and the stepped portion on the inner wall surface 33 b of the cylindrical hole 33.
- the annular space 37 is an annular groove having a rectangular cross section formed around the lid 62.
- the annular space 37 functions as an oil sump communicating with the separation chamber 42.
- the refrigerant gas discharged from the discharge chamber 26 is introduced into the separation chamber 42 through the introduction passage 40.
- the discharged refrigerant gas introduced into the separation chamber 42 flows toward the front of the cylindrical portion 63 while swirling along the inner wall surface 33b in the space between the inner wall surface 33b and the cylindrical portion 63.
- the mist-like oil contained in the discharged refrigerant gas is separated from the refrigerant gas by the action of the centrifugal force.
- the separated oil swirls in the separation chamber 42 due to the influence of the swirling refrigerant gas, but a part of the oil falls along the inner wall 33 b of the separation chamber 42 due to its own weight, and falls on the bottom of the separation chamber 42. It collects near the bottom of the lid 62.
- the discharged refrigerant gas from which the oil has been separated flows into the internal pipe 65 through the gas passage hole 63a formed in front of the cylindrical portion 63, and is then introduced into the check valve 36.
- the discharged refrigerant gas introduced into the check valve 36 is discharged toward the discharge flange 43 through the discharge passage 41.
- a lid 62 that partitions the separation chamber 42 and the discharge chamber 26, and a cylindrical portion 63 and a pedestal portion 64 having the function of the oil separator 35 are integrally formed so as to constitute a single member 61. of Thus, the number of parts can be reduced and the assembly can be simplified.
- the compressor according to the fourth embodiment shown in FIG. 6 is a modification of the method for forming the annular space in the compressor according to the first embodiment, and the compression according to the first embodiment
- the same components as those of the machine are denoted by the same reference numerals, and detailed description thereof is omitted.
- annular groove 71 having a square cross section is formed on the inner wall surface 33 b of the inlet portion of the cylindrical hole 33 formed in the rear housing member 14.
- the annular groove 71 is provided at a position communicating with the oil passage 39.
- the lid 72 includes a cylindrical outer ring portion 72a having a constant outer diameter in the axial direction, and does not have a flange portion.
- annular space 37 as an oil reservoir is formed between the outer peripheral surface of 72a. This annular space 37 functions as an oil reservoir communicating with the separation chamber 42.
- the annular groove 71 may be formed on the outer peripheral surface of the outer ring portion 72a in place of the rear housing member 14.
- a compressor according to the fifth embodiment shown in FIG. 7 is obtained by changing the configuration of the annular space as an oil reservoir in the compressor according to the third embodiment.
- the same components as those in the compressor are denoted by the same reference numerals, and detailed description thereof is omitted.
- a lid 74 and an oil separator 35 composed of a cylindrical portion 75 and a pedestal portion 76 are configured as an integrally formed member 73.
- the member 73 is disposed in the cylindrical hole 33 in a state where the check valve 36 is attached to the opening side (right side in the figure) of the pipe line 77 formed inside the oil separator 35.
- the lid 74 is formed in a flange shape, the cylindrical portion 75 has a large diameter portion 75a and a small diameter portion 75b, and the small diameter portion 75b is disposed between the lid 74 and the large diameter portion 75a.
- the cylindrical hole 33 has a large-diameter enlarged hole 33a on the side that opens to the discharge chamber 26.
- the enlarged-diameter hole 33a extends to the vicinity of the large-diameter portion 75a of the cylindrical portion 75 in the axial direction. Therefore, the region on the lid 74 side in the separation chamber 78 defined by the member 73 and the enlarged diameter hole 33a and the inner wall surface 33b of the cylindrical hole 33 forms an annular space 79 that is larger than the others.
- Annular space 7 9 functions as an oil reservoir communicating with the separation chamber 78.
- the member 73 is fixed to the cylindrical hole 33 by press-fitting the pedestal portion 76 to the inner wall surface 33b and the lid 74 to the enlarged diameter hole 33a.
- Four gas passage holes 75c extending in a direction perpendicular to the central axis of the pipe line 77 are disposed in the small diameter portion 75b and open to the separation chamber 78. It is preferable that the gas passage hole 75c is disposed as close to the large diameter portion 75a as possible.
- the oil passage 39 has a size that is a predetermined throttle so that the high-pressure refrigerant gas in the force separation chamber 78 does not flow into the oil storage chamber 47 side that opens directly to the top of the annular passage 79 that is an oil reservoir. It is set.
- the refrigerant gas introduction passage 40 that connects the discharge chamber 26 and the separation chamber 78 is provided in the rear housing member 14 that forms the cylindrical hole 33 so as to be inclined with respect to the central axis of the pipe line 77. An opening is made so as to face the large diameter portion 75a.
- the high-pressure refrigerant gas introduced from the discharge chamber 26 into the separation chamber 78 via the introduction passage 40 is the first embodiment.
- the oil swirls around the large-diameter portion 75a, and the oil contained in the refrigerant gas is centrifuged.
- the separated oil gathers in the vicinity of the wall surface of the lid 74 and the enlarged diameter hole 33a while turning in the annular space 79. Part of the oil falls due to its own weight and also accumulates in the lower part of the annular space 79 (lower part of Fig. 7).
- the oil G gathering while turning near the wall of the upper part of the annular space 79 flows into the oil storage chamber 47 through the oil passage 39 by the differential pressure.
- the oil G accumulated on the lower wall surface of the annular space 79 is gradually wound up by the swirling flow in the annular space 79 and is sequentially discharged from the oil passage 39 to the oil storage chamber 47.
- the compressor according to the fifth embodiment has the following advantages in addition to the advantages of the third embodiment.
- the compressor according to the sixth embodiment shown in FIG. 8 is obtained by changing the configuration of the lid 34 in the first embodiment, and has the same configuration as the compressor according to the first embodiment. Are denoted by the same reference numerals, and detailed description thereof is omitted.
- the inner wall surface 33 b of the cylindrical hole 33 has a constant diameter in the axial direction and opens into the discharge chamber 26.
- the lid 80 is made of a plate material formed by press-caching a thin steel plate and has a cylindrical outer ring portion 81.
- the material of the lid 80 is not limited to an iron plate, but can be replaced with other rigid materials, and can be formed by molding.
- the outer ring portion 81 is provided with a throttle passage 82 at a position corresponding to the oil passage 39 disposed on the upper part of the rear housing member 14 (above FIG. 8), and the lid 80 is fixed to the inner wall surface 33b by press-fitting.
- the oil passage 39 and the throttle passage 82 are configured to match! RU
- the throttle passage 82 and the oil passage 39 are formed to have the same diameter. However, if the throttle passage 82 is large enough to exhibit the throttling effect, the oil passage 39 is easy to process.
- the diameter may be larger than that of the throttle passage 82 so that the oil can easily flow.
- the length of the end surface force on the discharge chamber 26 side of the lid 80 to the throttle passage 82 needs to have a sealing function between the discharge chamber 26 and the following separation chamber 83, but the length is shortened as much as possible. It is preferable to keep the entrance of the throttle passage 82 as far as possible from the entrance 35d of the conduit 35c.
- the base portion 35b of the oil separator 35 to which the check valve 36 is attached is press-fitted into the cylindrical hole 33, and the outer ring portion 81 of the lid 80 is further press-fitted into the cylindrical hole 33, whereby the oil separator 35 and the lid 80 Is formed along the inner peripheral surface of the outer ring portion 81 of the lid 80.
- An oil sump 84 is formed. This oil sump 84 functions as an oil sump communicating with the separation chamber 83.
- the high-pressure refrigerant gas in the discharge chamber 26 passes through the introduction passage 40, and is supplied to the cylindrical portion 35a of the oil separator 35.
- the oil is centrifuged by the transfer.
- the refrigerant gas from which the oil has been separated flows from the inlet 35d into the pipe line 35c, and by the pressure, the check valve 36 is pushed open and flows into the discharge passage 41.
- Refrigerant gas force The separated oil G is affected by the swirling flow of the refrigerant gas and swirls around the oil reservoir 84, and a part of the oil G accumulates under the oil reservoir 84 (downward in FIG. 8) due to its own weight. Therefore, of the swirling oil, the oil G present in the upper part of FIG. 8 is squeezed by the differential pressure, flows through the passage 82 to the oil passage 39, and is discharged to the oil storage chamber 47 (see FIG. 1).
- the compressor according to the sixth embodiment has the following advantages.
- the compressor according to the seventh embodiment shown in FIG. 9 is obtained by changing the configuration of the lid in the compressor according to the first embodiment and the sixth embodiment.
- the same components as those of the compressor according to the embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.
- a step is formed by the enlarged diameter hole 33a following the inner wall surface 33b of the cylindrical hole 33 constituting the discharge passage, and the oil passage 39 communicating with the oil storage chamber 47 (see FIG. 1) is enlarged.
- the configuration of opening in the vicinity of the stepped portion of the hole 33a is the same as that of the compressor according to the first embodiment.
- the lid 85 is a plate material formed by pressing an iron plate in the same manner as the compressor according to the sixth embodiment, but can be formed by other materials and processing methods.
- the lid 85 is formed in a bottomed cylindrical shape, and includes a large-diameter flange portion 85a and an outer ring portion 85b having the same outer diameter as the inner diameter of the inner wall surface 33b.
- the high-pressure refrigerant gas in the discharge chamber 26 passes through the introduction passage 40, is supplied to the cylindrical portion 35a of the oil separator 35, and moves to the lid 85 side while turning around the periphery. Is centrifuged.
- the flow of the refrigerant gas from which the oil has been separated is the same as in the first and sixth embodiments.
- the oil G separated from the refrigerant gas column receives the swirling flow of the refrigerant gas, swirls the inner circumference of the outer ring portion 85b, and partly falls due to its own weight, and the lower part of the outer ring portion 85b (Fig. 8). It is easy to collect in the lower part of).
- the oil G collected in the lower part of the outer ring portion 85b flows into the annular space 86 through the throttle passage 87, and is further discharged from the annular space 86 to the oil storage chamber 47 (see FIG. 1) through the oil passage 39 by the differential pressure. . Therefore, the compressor according to the seventh embodiment can exhibit a synergistic advantage in which the advantages of the compressors according to the first embodiment and the sixth embodiment are combined.
- the compressor according to the eighth embodiment shown in FIG. 10 has the same configuration as that of the compressor according to the first embodiment, since the configuration according to the first embodiment is changed. The detailed explanation is omitted.
- the oil separator 90 is integrally formed with the rear housing member 14.
- an inner wall 89 of a discharge passage 88 extending in the axial direction of the drive shaft of the compressor has a constant diameter in the axial direction.
- the cylindrical oil separator 90 is integrally formed with the rear housing member 14 so as to protrude into the discharge passage 88.
- the rear housing member 14 includes a discharge passage 91 that allows the separation chamber 42 and the high-pressure fluid chamber 44 to communicate with each other, and the discharge passage 91 is formed by a through hole that is bent in a V shape.
- the discharge passage 91 includes a pipe line 90b extending horizontally from the tip of the oil separator 90 along the axis of the oil separator 90 toward the rear side of the rear housing member 14, and an obliquely upper side of the rear housing member 14 from the pipe line 90b. And a portion extending toward the surface.
- Pipe line 90b is attached to the tip of oil separator 90. It has an open inlet 90a.
- An oil passage 39 having an appropriate throttling function opens above the inner wall 89 (upper side
- a plate-like lid 92 is fixed to the inner wall 89 of the discharge passage 88 by press fitting.
- the position of the lid 92 is set so that the inner end face thereof coincides with the opening of the oil passage 39.
- a space between the lid 92 and the oil separator 90 is formed as a separation chamber 93, and an oil sump 94 defined by the inner end face of the lid 92 and the inner wall 89 is formed.
- This oil sump 94 functions as an oil sump communicating with the separation chamber 93.
- the check valve 36 shown in the first embodiment may be provided in a passage at an appropriate position reaching the discharge passage 91 or the external refrigerant circuit 48.
- the high-pressure refrigerant gas in the discharge chamber 26 is supplied from the introduction passage 40 to the outer peripheral surface of the oil separator 90, and the oil moves in a process of spirally turning in the direction of the lid 92. Centrifuge.
- the refrigerant gas from which the oil has been separated is discharged from the inlet 90a to the external refrigerant circuit 48 through the pipe line 90b and the discharge passage 91.
- the oil G that is swirled in the oil reservoir 94 and exists in the upper part is discharged from the oil passage 39 to the oil storage chamber 47 by the differential pressure.
- the compressor according to the eighth embodiment significantly reduces the number of parts and assembly man-hours for configuring the oil separation device. Also has the advantage that it can be simplified.
- the compressor according to the ninth embodiment shown in FIGS. 11 and 12 is obtained by changing a part of the configuration of the compressor according to the first embodiment, and therefore has the same configuration as the compressor. Are given the same reference numerals, and detailed description is omitted.
- a step 33c for forming the throttle passage 38 is formed in the cylindrical hole 33, and the oil passage 39 communicates with the annular space where the side surface of the lid 34 is desired.
- the compressor according to the ninth embodiment has an oil ring passage that supplies oil from the oil storage chamber 47 to the suction chamber 25 that is a low pressure region.
- an inner wall surface 33 b of the cylindrical hole 33 has a constant diameter in the axial direction and opens into the discharge chamber 26.
- the lid 95 is also a columnar metal member corresponding to the diameter of the cylindrical hole 33, and an annular groove 96 is formed on the outer peripheral surface 95a of the lid 95 as shown in FIG.
- the groove 96 constitutes an oil intermediate passage 100 that is a part of the oil ring passage 97 and corresponds to an oil throttle portion in the oil ring passage 97.
- the groove 96 is easily formed by cutting with a lathe or pressing with a press.
- the lid 95 is fixed to the cylindrical hole 33 by press fitting, and the separation chamber 42 is Partition. When the lid 95 is fixed, a sealed oil intermediate passage 100 surrounded by the groove 96 and the inner wall surface 33b of the separation chamber 42 is formed.
- the oil ring passage 97 includes a sealed oil intermediate passage 100 formed by the groove 96 and the inner wall surface 33b, an oil upstream passage 98 that allows the oil storage chamber 47 to communicate with the groove 96, and the groove 96 as a suction chamber. 25 and an oil downstream passage 99 communicating with 25.
- the oil upper passage 98 and the oil downstream passage 99 are formed in the rear housing member 14.
- the cross-sectional area of the oil upstream passage 98 and the oil downstream passage 99 is set larger than the cross-sectional area of the oil intermediate passage 100. Therefore, the oil intermediate passage 100 functions as an oil throttle portion in the oil ring passage 97.
- the passage cross-sectional area of the groove 96 is determined according to the performance of the compressor.
- the cross-sectional areas of the oil upstream passage 98 and the oil downstream passage 99 may be set according to production technology.
- the oil passing through the oil ring flow path 97 flows along the inner wall surface 33b covering the groove 96 in the oil intermediate passage 100 V.
- a part of the oil ring passage 97 can be easily formed by simply swaging the groove 96 on the outer peripheral surface 95a of the lid 95.
- An oil intermediate passage 100 can be formed.
- An oil ring channel 97 through the lid 95 can be formed. Furthermore, handling of the oil ring passage 97 is facilitated.
- the oil throttle section determines the amount of oil supplied from the oil storage chamber 47 to the suction chamber 25 by the throttle effect, and the oil throttle section allows the refrigerant gas to pass from the oil storage chamber 47 to the suction chamber 25. It can be prevented.
- the oil throttle portion is formed in the oil intermediate passage 100, the oil throttle portion can be easily formed in combination with the easy formation of the oil intermediate passage 100. Small passage area! /! Easy to set the accuracy of the oil throttle even when forming the oil throttle.
- a compressor according to the tenth embodiment shown in FIG. 13 is obtained by changing the configuration of the lid and the oil intermediate passage in the compressor according to the ninth embodiment.
- the same components as those in the compressor according to the ninth embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.
- the lid 101 of the compressor according to this embodiment is press-fitted into the cylindrical hole 33, but no groove is formed on the outer peripheral surface 101a of the lid 101.
- An annular groove 102 is formed in a portion of the inner wall surface 33b of the separation chamber 42 where the outer peripheral surface 101a contacts. That is, the annular groove 102 is formed in the rear housing member 14.
- the groove 102 constitutes an oil intermediate passage 100 which is a part of the oil ring passage 97 and corresponds to an oil throttle portion in the oil ring passage 97.
- the groove 102 is easily formed by cutting with a lathe.
- the oil ring passage 97 includes an oil intermediate passage 100, an oil upstream passage 98 that connects the oil storage chamber 47 to the groove 102, and an oil downstream passage 99 that connects the groove 102 to the suction chamber 25 that is a low pressure region. including.
- the oil upstream passage 98 and the oil downstream passage 99 are only partially shown in FIG.
- the passage sectional area of the groove 102 is smaller than the passage sectional areas of the oil upstream passage 98 and the oil downstream passage 99.
- the oil intermediate passage 100 functions as an oil throttle part in the oil ring passage 97.
- the oil passing through the oil ring passage 97 flows along the outer peripheral surface 101a of the lid 101 that covers the groove 102 in the oil intermediate passage 100.
- the compressor according to the tenth embodiment has the same advantages as the advantages (2) and (3) of the compressor according to the ninth embodiment.
- the oil intermediate passage 100 can be easily formed simply by machining the groove 102 in the force inner wall surface 33b provided with the oil circulation passage 97 for supplying oil from the oil storage chamber 47 to the suction chamber 25. Further, since the oil intermediate passage 100 is easily formed, the oil ring passage 97 can be easily handled.
- a compressor lid 105 according to the eleventh embodiment shown in FIG. 14 is obtained by changing the configurations of the compressor lid and the oil intermediate passage according to the ninth embodiment.
- the same components as those of the compressor according to the ninth embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.
- the lid 105 shown in FIG. 14 has a through hole 106 that traverses the inside in the radial direction.
- the through hole 106 is linear, and the through hole 106 constitutes an oil intermediate passage 100 that is a part of the oil ring flow path 97, and corresponds to a sealed oil throttle portion in the oil ring flow path 97.
- the openings at both ends of the through-hole 106 are respectively disposed on the outer peripheral surface 105a of the lid 105, and both the openings exist at positions corresponding to the opening positions of the oil upstream passage 98 and the oil downstream passage 99 on the inner wall surface 33b.
- the direction of the through hole 106 is adjusted to the opening positions of the oil upstream passage 98 and the oil downstream passage 99, and then the lid 105 is press-fitted into the cylindrical hole 33.
- the through hole 106 is easily formed by, for example, drilling.
- the passage sectional area of the through hole 106 is smaller than the passage sectional areas of the oil upper passage 98 and the oil downstream passage 99. This is to make the through hole 106 function as an oil throttle part in the oil ring flow path 97. Oil passing through the oil ring passage 97 flows through the through hole 106 in the oil intermediate passage 100.
- the compressor according to the eleventh embodiment has the same advantages as the advantages (2) and (3) of the compressor according to the ninth embodiment. Further, the oil intermediate passage 100 can be easily formed simply by machining the through hole 106 in the force lid 105 provided with the oil ring passage 97 for supplying oil from the oil storage chamber 47 to the suction chamber 25 which is a low pressure region. it can. Accordingly, the oil ring passage 97 can be easily handled.
- the passage sectional area of the oil throttle portion can be set with high accuracy. Since the oil throttle part that passes through the inside of the lid 105 is formed, the lid 105 is more firmly fixed to the rear housing member 14 by press-fitting compared to the case where the oil throttle part is formed on the outer peripheral surface 105a of the lid 105. It can be maintained firmly. In addition, oil in the oil ring passage 97 is unlikely to leak into the separation chamber 72 and the discharge chamber 25.
- a lid 110 shown in FIG. 15 (a) has a cylindrical outer ring portion 111, and the outer ring portion 111 is formed by, for example, pressing a metal plate.
- a small-diameter portion that is bent toward the radial center is formed in the axially intermediate portion of the outer ring portion 111, and a groove 112 is formed on the outer peripheral surface of the outer ring portion 111 corresponding to the small-diameter portion.
- the lid 115 shown in FIG. 15 (b) is fixed to the cylindrical hole 33 not by press fitting but by a snap ring.
- the cylindrical hole 33 has a large diameter portion 331 corresponding to the diameter of the lid 115 and a small diameter portion 332 smaller than the diameter of the lid 115, and a step 333 is formed between the large diameter portion 331 and the small diameter portion 332. It is.
- the lid 115 is cylindrical, and a sealing groove 117 is formed on both axial sides of the outer peripheral surface 115a of the lid 115, and a groove 116 as an oil intermediate passage 100 is formed between the sealing grooves 117. Yes.
- annular groove 334 for a snap ring is formed near the opening of the inner wall surface 331a of the large diameter portion 331.
- the sealing member 118 is attached to the sealing groove 117 of the lid 115, and the lid 115 is inserted into the large-diameter portion 331 until it hits the step 333. Then, by attaching the snap ring 119 to the annular groove 334, the lid 115 is prevented from falling off from the cylindrical hole 33. Since the seal member 118 is provided, the oil in the oil circulation passage 97 hardly leaks into the separation chamber 42 or the discharge chamber 26.
- FIG. 16 The first different example shown in FIG. 16 is partially in common with the configurations of the compressors according to the first and ninth embodiments.
- the components common to the compressors according to the first and ninth embodiments are denoted by the same reference numerals, and detailed description thereof is omitted.
- a step 33c for forming the throttle passage 38 is formed in the cylindrical hole 33, the oil passage 39 communicates with the annular space facing the outer peripheral surface of the lid 120, and the oil storage chamber 47 is connected to the low pressure region.
- An oil circulation passage 97 for supplying oil to the suction chamber 25 is provided.
- the inlet of the cylindrical hole 33 (left side in Fig. 16) has a diameter larger than the diameter of the cylindrical hole 33.
- An enlarged diameter hole 33a is formed.
- a lid 120 that partitions the discharge chamber 26 and the discharge passage formed by the cylindrical hole 33 is attached to the inlet.
- the lid 120 has a flange portion 120a and an outer ring portion 120b, and a stepped portion is formed on the outer peripheral surface 120c of the lid 120 by the flange portion 120a and the outer ring portion 120b.
- the lid 120 is fixed to the cylindrical hole 33 by fitting the outer ring portion 120b to the inner wall surface 33b of the cylindrical hole 33 and fitting the flange portion 120a to the enlarged diameter hole 33a.
- An annular space 37 is formed by the outer ring portion 120b and the enlarged diameter hole 33a.
- An annular groove 121 is formed on the outer peripheral surface 120c of the lid 120 corresponding to the flange portion 120a.
- the groove 121 constitutes an oil intermediate passage 100 that is a part of the oil ring passage 97, and corresponds to an oil throttle portion in the oil ring passage 97.
- the oil ring passage 97 includes a sealed oil intermediate passage 100 formed by the groove 121 and the inner wall surface, an oil upstream passage 98 that connects the oil storage chamber 47 and the groove 121, and a suction chamber that is the low pressure region of the groove 121. And an oil downstream passage 99 communicating with the oil downstream passage.
- the oil G separated from the discharged refrigerant gas and stored in the bottom portion of the separation chamber 42 flows toward the annular space 37 through the throttle passage 38 and further into the oil passage 39. Is supplied to the oil storage chamber 47.
- the oil in the oil storage chamber 47 is supplied to the suction chamber 25 through the oil circulation passage 97.
- FIG. 17 a second alternative example shown in FIG. 17 will be described.
- the second alternative example is partly in common with the configuration of the compressor according to the second and ninth embodiments.
- the components common to the compressors according to the second and ninth embodiments are denoted by the same reference numerals, and detailed description thereof is omitted.
- a throttle passage 127 is formed in the lid 125, the oil passage 39 communicates with the annular space 37 facing the outer peripheral surface 125c of the lid 125, and the low pressure region from the oil storage chamber 47.
- An oil ring passage 97 for supplying oil to the suction chamber 25 is provided.
- An enlarged diameter hole 33a having a diameter larger than the diameter of the cylindrical hole 33 is formed at the inlet of the cylindrical hole 33 (left side in FIG. 17).
- the lid 125 has a flange portion 125a and an outer ring portion 125b, and a stepped portion is formed on the outer peripheral surface 125c of the lid 125 by the flange portion 125a and the outer ring portion 125b.
- the outer ring portion 125 b of the lid 125 is fixed to the cylindrical hole 33.
- An annular groove 126 is formed on the outer peripheral surface 125c corresponding to the flange portion 125a.
- the groove 126 constitutes an oil intermediate passage 100 that is a part of the oil ring passage 97, and corresponds to an oil throttle portion in the oil ring passage 97.
- the throttle passage 127 in this embodiment is formed by a through hole 128 that is provided at the lowermost position of the outer ring portion 125b of the lid 125 and extends in a direction perpendicular to the axis of the lid 125 (upward in FIG. 17). Has been.
- This throttle passage 127 allows the separation chamber 42 to communicate with the annular space 37. Accordingly, the oil G separated from the discharged refrigerant gas and stored in the bottom portion of the separation chamber 42 flows toward the annular space 37 through the throttle passage 127 and is further supplied to the oil storage chamber through the oil passage 39. Oil in the oil storage chamber is supplied to the suction chamber through the oil ring passage 97.
- the discharge passage described in the first to eighth embodiments may be disposed so as to extend obliquely with respect to the axial direction of the compressor, and an oil separator may be disposed in the discharge passage.
- the lid in the first to fourth embodiments may be fixed to the round hole by press-fitting.
- the pedestal portions 64 and 76 may be fixed to the cylindrical hole 33 by press fitting, and seal members may be provided on the outer peripheral surfaces of the lids 62 and 74.
- seal members may be provided on the outer peripheral surfaces of the lids 62 and 74.
- the seal member is not limited to the outer peripheral surface of the lids 62 and 74, and may be provided between the stepped portion formed on the inner wall surface 33b of the cylindrical hole 33 and the end surfaces of the lids 62 and 74.
- the oil passage 39 may be provided in the lower part of the oil reservoir.
- the oil storage chamber is provided above the separation chamber.
- the oil storage chamber can be arranged at the most appropriate position such as next to or below the separation chamber.
- the step formed on the inner wall surface of the round hole constituting the discharge passage, the outer peripheral surface of the lid, or both may be formed in a tapered shape. Good.
- the gas passage holes 63a and 75c in the first and fifth embodiments are forces extending at right angles to the central axes of the pipes 65 and 77, as long as they intersect the central axis and are not perpendicular to the central axis. It may extend to form an angle of. There are 4 gas passage holes 63a and 75c. Although what was provided in the place was shown, it is possible to arrange in multiple places other than four places.
- the cross-sectional shape of the annular space formed around the lid is a quadrangle, but the cross-sectional triangle is not limited to this and may be a triangle.
- the cross section may be round or oval. In short, if oil can be passed
- the annular space may have any cross-sectional shape.
- the throttle passage provided in the lower portion of the lid is formed by providing a step portion on the inner wall surface of the separation chamber. You may form by providing.
- a force for increasing the thickness of the lid 92 may be configured such that a part of the lid 92 protrudes toward the opening of the oil passage 39 by providing the lid 92 with a flange portion. This makes it possible to reduce the opening of the oil passage 39 and enhance the throttling effect.
- the oil intermediate passage in the oil ring passage is made to function as the oil throttle portion in order to easily form the oil throttle portion.
- the oil throttle passage that does not function as an oil throttle section may be freely set in the middle of the oil circulation passage.
- an oil throttle part may be provided in the oil upstream passage or the oil downstream passage.
- the compressor has been described as a variable displacement swash plate compressor, but the compressor may be a fixed displacement type or a wobble type.
- the compressor is not limited to the swash plate type, but may be a scroll type or a vane type.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007530533A JP4840363B2 (ja) | 2006-03-29 | 2007-03-20 | 圧縮機 |
EP20070739074 EP2000672B1 (en) | 2006-03-29 | 2007-03-20 | Compressor |
US12/095,424 US8991296B2 (en) | 2006-03-29 | 2007-03-20 | Compressor |
CN2007800012242A CN101356367B (zh) | 2006-03-29 | 2007-03-20 | 压缩机 |
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006-089907 | 2006-03-29 | ||
JP2006089907 | 2006-03-29 | ||
JP2006-147585 | 2006-05-29 | ||
JP2006147585 | 2006-05-29 | ||
JP2006-342055 | 2006-12-20 | ||
JP2006342055 | 2006-12-20 |
Publications (1)
Publication Number | Publication Date |
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WO2007111194A1 true WO2007111194A1 (ja) | 2007-10-04 |
Family
ID=38541114
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2007/055631 WO2007111194A1 (ja) | 2006-03-29 | 2007-03-20 | 圧縮機 |
Country Status (6)
Country | Link |
---|---|
US (1) | US8991296B2 (ja) |
EP (2) | EP2000672B1 (ja) |
JP (1) | JP4840363B2 (ja) |
KR (1) | KR100912846B1 (ja) |
CN (1) | CN101356367B (ja) |
WO (1) | WO2007111194A1 (ja) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
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EP2093423A1 (en) * | 2008-02-21 | 2009-08-26 | Kabushiki Kaisha Toyota Jidoshokki | Clutchless swash plate compressor |
WO2010151019A2 (ko) * | 2009-06-26 | 2010-12-29 | 두원공과대학교 | 체크 밸브 및 이를 구비하는 압축기 |
DE112011102086T5 (de) | 2010-06-21 | 2013-07-18 | Sanden Corporation | Taumelscheibenkompressor |
US9797638B2 (en) | 2012-11-07 | 2017-10-24 | Sanden Holdings Corporation | Compressor |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5692177B2 (ja) * | 2012-07-19 | 2015-04-01 | 株式会社豊田自動織機 | 圧縮機 |
JP5920367B2 (ja) * | 2013-07-18 | 2016-05-18 | 株式会社豊田自動織機 | 片頭ピストン式可変容量型圧縮機 |
WO2015062676A1 (en) | 2013-11-04 | 2015-05-07 | Carrier Corporation | Refrigeration circuit with oil separation |
KR102018259B1 (ko) * | 2014-02-24 | 2019-09-05 | 한온시스템 주식회사 | 압축기 |
JP6241440B2 (ja) * | 2014-06-18 | 2017-12-06 | 株式会社豊田自動織機 | 圧縮機 |
KR20170008602A (ko) * | 2015-07-14 | 2017-01-24 | 한온시스템 주식회사 | 양두 사판식 압축기 |
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- 2007-03-20 WO PCT/JP2007/055631 patent/WO2007111194A1/ja active Application Filing
- 2007-03-20 KR KR1020087009897A patent/KR100912846B1/ko active IP Right Grant
- 2007-03-20 CN CN2007800012242A patent/CN101356367B/zh not_active Expired - Fee Related
- 2007-03-20 US US12/095,424 patent/US8991296B2/en not_active Expired - Fee Related
- 2007-03-20 EP EP20070739074 patent/EP2000672B1/en not_active Not-in-force
- 2007-03-20 EP EP14150729.3A patent/EP2719898B1/en not_active Ceased
- 2007-03-20 JP JP2007530533A patent/JP4840363B2/ja not_active Expired - Fee Related
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Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2093423A1 (en) * | 2008-02-21 | 2009-08-26 | Kabushiki Kaisha Toyota Jidoshokki | Clutchless swash plate compressor |
WO2010151019A2 (ko) * | 2009-06-26 | 2010-12-29 | 두원공과대학교 | 체크 밸브 및 이를 구비하는 압축기 |
WO2010151019A3 (ko) * | 2009-06-26 | 2011-04-21 | 두원공과대학교 | 체크 밸브 및 이를 구비하는 압축기 |
KR101099117B1 (ko) * | 2009-06-26 | 2011-12-27 | 주식회사 두원전자 | 체크 밸브 및 이를 구비하는 압축기 |
DE112011102086T5 (de) | 2010-06-21 | 2013-07-18 | Sanden Corporation | Taumelscheibenkompressor |
US9011109B2 (en) | 2010-06-21 | 2015-04-21 | Sanden Corporation | Variable Capacity Compressor |
DE112011102086B4 (de) | 2010-06-21 | 2020-01-09 | Sanden Holdings Corporation | Taumelscheibenkompressor mit Öllagerkammer |
US9797638B2 (en) | 2012-11-07 | 2017-10-24 | Sanden Holdings Corporation | Compressor |
DE112013005321B4 (de) * | 2012-11-07 | 2019-11-14 | Sanden Holdings Corporation | Kompressor |
Also Published As
Publication number | Publication date |
---|---|
CN101356367A (zh) | 2009-01-28 |
EP2719898B1 (en) | 2017-07-19 |
KR100912846B1 (ko) | 2009-08-18 |
EP2000672A4 (en) | 2013-06-26 |
EP2719898A3 (en) | 2014-07-02 |
EP2719898A2 (en) | 2014-04-16 |
KR20080055951A (ko) | 2008-06-19 |
JPWO2007111194A1 (ja) | 2009-08-13 |
EP2000672A1 (en) | 2008-12-10 |
JP4840363B2 (ja) | 2011-12-21 |
CN101356367B (zh) | 2010-09-08 |
US8991296B2 (en) | 2015-03-31 |
US20100018386A1 (en) | 2010-01-28 |
EP2000672B1 (en) | 2015-05-06 |
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