US20230064536A1 - Compressor and air conditioner - Google Patents
Compressor and air conditioner Download PDFInfo
- Publication number
- US20230064536A1 US20230064536A1 US17/654,437 US202217654437A US2023064536A1 US 20230064536 A1 US20230064536 A1 US 20230064536A1 US 202217654437 A US202217654437 A US 202217654437A US 2023064536 A1 US2023064536 A1 US 2023064536A1
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- United States
- Prior art keywords
- face part
- rotating shaft
- face
- muffler
- discharge valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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- 230000007246 mechanism Effects 0.000 claims abstract description 33
- 239000003507 refrigerant Substances 0.000 claims description 67
- 230000002265 prevention Effects 0.000 claims description 2
- 238000000926 separation method Methods 0.000 claims description 2
- 239000012808 vapor phase Substances 0.000 description 25
- 230000006835 compression Effects 0.000 description 18
- 238000007906 compression Methods 0.000 description 18
- 239000007791 liquid phase Substances 0.000 description 9
- 238000005192 partition Methods 0.000 description 8
- 239000012071 phase Substances 0.000 description 7
- 239000007788 liquid Substances 0.000 description 5
- 239000010687 lubricating oil Substances 0.000 description 5
- 238000001816 cooling Methods 0.000 description 4
- 238000010438 heat treatment Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 239000003921 oil Substances 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000005489 elastic deformation Effects 0.000 description 3
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- 238000005452 bending Methods 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
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- 239000000463 material Substances 0.000 description 2
- 238000003825 pressing Methods 0.000 description 2
- 230000003014 reinforcing effect Effects 0.000 description 2
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- ZAMOUSCENKQFHK-UHFFFAOYSA-N Chlorine atom Chemical compound [Cl] ZAMOUSCENKQFHK-UHFFFAOYSA-N 0.000 description 1
- 229910000639 Spring steel Inorganic materials 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 239000006096 absorbing agent Substances 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000001174 ascending effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 229910052801 chlorine Inorganic materials 0.000 description 1
- 239000000460 chlorine Substances 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
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- 238000006467 substitution reaction Methods 0.000 description 1
Images
Classifications
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- 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
- F04C29/06—Silencing
- F04C29/065—Noise dampening volumes, e.g. muffler chambers
-
- 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
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
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- 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
- F04C23/001—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 of similar working principle
-
- 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
- F04C29/06—Silencing
- F04C29/068—Silencing the silencing means being arranged inside the pump housing
-
- 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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
- F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
-
- 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
- F04C2240/50—Bearings
-
- 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
Definitions
- Embodiments described herein relate generally to a compressor and air conditioner including the compressor.
- a refrigerating cycle device such as an air conditioner or the like is equipped with a compressor configured to compress the refrigerant.
- the compressor includes, as main components, for example, an electric-motor unit configured to rotate, for example, a rotating shaft, compression-mechanism unit coupled to the electric-motor unit through the rotating shaft, and airtight container accommodating therein the electric-motor unit and compression-mechanism unit.
- the electric-motor unit includes, for example, a so-called inner-rotor type motor and includes a rotor firmly fixed to the rotating shaft and stator fixed to the inner circumferential part of the airtight container.
- the rotating shaft includes crank parts (eccentric parts).
- the compression-mechanism unit includes cylinders each forming, for example, cylinder chambers, and rollers fitted onto the eccentric parts of the rotating shaft and eccentrically rotated inside the cylinder chambers.
- the inside of the cylinder chamber is partitioned into a suction chamber and compression chamber of the refrigerant with a vane.
- the rotating shaft is rotatably supported with bearings.
- the bearing includes a flange part defining a surface in the cylinder chamber in the axial direction of the rotating shaft, and boss part extending in a cylindrical form from the flange part.
- a muffler configured to suppress pulsation and noise caused by the refrigerant to be compressed by the cylinder of the compression-mechanism unit and discharged into the airtight container is attached to the bearing.
- the flange part includes a discharge port from which the refrigerant compressed by the cylinder is discharged into the airtight container, and discharge valve mechanism configured to control opening/closing of the discharge port.
- the flange part includes a concave part (dug-down part) in which the discharge valve mechanism is to be installed in the vicinity of the discharge port.
- the dug-down part is formed by digging down one surface in the bearing in the axial direction of the rotating shaft, for example, the top surface of the flange part to a predetermined depth. Accordingly, the dug-down part has a less thickness as compared with other portions of the flange part, and the rigidity thereof is liable to become relatively lower in the bearing.
- the dug-down part when the rotating shaft is rotated, there is a possibility of the dug-down part being elastically deformed in such a manner as to incline the boss part toward, for example, the flange part.
- the support rigidity of the rotating shaft based on the bearings being lowered, and possibility of the rotating shaft causing bending vibration and enhancing the noise.
- FIG. 1 is a circuit diagram schematically showing the configuration of an air conditioner according to an embodiment.
- FIG. 2 is a vertical cross-sectional view of a compressor according to the embodiment.
- FIG. 3 is a view schematically showing a bearing (first bearing including a first discharge valve mechanism) including a discharge valve mechanism of the compressor according to the embodiment from above.
- FIG. 4 is a view schematically showing the cross section of the bearing (first bearing) at the part indicated by the arrows A 3 shown in FIG. 3 .
- FIG. 5 is a view schematically showing, from above, the state where a muffler (first muffler) of the compressor according to the embodiment is mounted on the bearing (first bearing).
- FIG. 6 is a perspective view schematically showing the muffler (first muffler) of the compressor according to the embodiment.
- a compressor comprises cylinders, a rotating shaft, bearings, at least one of discharge valve mechanisms, and at least one of mufflers.
- the cylinders compress a refrigerant.
- a rotating shaft arranges inside the cylinders and includes eccentric parts.
- Each of the bearings includes a flange part defining a surface in the cylinder in an axial direction of the rotating shaft, and a boss part extending in a cylindrical form concentric with the rotating shaft so as to be continuous with the flange part and rotatably supporting the rotating shaft.
- At least one of the discharge valve mechanisms is arranged in the flange part and includes a discharge valve deformed to be opened when the refrigerant compressed by the cylinder reaches a predetermined discharge pressure and lengthwise in a predetermined direction, and a valve presser suppressing further deformation of the discharge valve when the discharge valve is opened.
- At least one of the mufflers covers the bearing so as to surround a part between the flange part and the boss part and forms, between the flange part and the boss part, a muffler chamber into which the refrigerant compressed by the cylinder is discharged.
- an outer contour of the muffler chamber is defined by each of an end face part which is a face part on one end side of the muffler in the axial direction of the rotating shaft, a brim part which is a face part on the other end side in the axial direction of the rotating shaft, and a side face part which joins the end face part and the brim part to each other in a cylindrical form throughout the entire circumference in the circumferential direction of the rotating shaft, and at least one of the mufflers includes a concave part formed by denting each of the end face part and the side face part toward the inside of the muffler chamber.
- FIGS. 1 to 6 An embodiment will be described hereinafter with reference to FIGS. 1 to 6 .
- FIG. 1 is a refrigerating cycle circuit diagram of an air conditioner 1 according to this embodiment.
- the air conditioner 1 is a device configured to carry out air conditioning on the basis of such a refrigerating cycle and is an example of the refrigerating cycle device.
- the air conditioner 1 includes, as main components, a compressor 2 , four-way valve 3 , outdoor heat exchanger 4 , outdoor heat exchanger 4 , outdoor air blower 40 , expanding device 5 , indoor heat exchanger 6 , and indoor air blower 60 .
- the discharge side of the compressor 2 is connected to a first port 3 a of the four-way valve 3 .
- a second port 3 b of the four-way valve 3 is connected to the outdoor heat exchanger 4 .
- the outdoor heat exchanger 4 is connected to the indoor heat exchanger 6 through the expanding device 5 .
- the indoor heat exchanger 6 is connected to a third port 3 c of the four-way valve 3 .
- a fourth port 3 d of the four-way valve 3 is connected to the suction side of the compressor 2 through an accumulator 8 .
- the refrigerant circulates through a circulation circuit 7 from the discharge side of the compressor 2 to the suction side thereof through the outdoor heat exchanger 4 , expanding device 5 , indoor heat exchanger 6 , and accumulator 8 .
- a refrigerant containing no chlorine is desirable and, for example, R448A, R449A, R449B, R407G, R407H, R449C, R456A, R516A, R406B, R463A, R744, and HC-based refrigerant and the like are applicable.
- the four-way valve 3 is switched in such a manner that the first port 3 a communicates with the second port 3 b , and third port 3 c communicates with the fourth port 3 d .
- the high-temperature/high-pressure vapor-phase refrigerant compressed by the compressor 2 is discharged into the circulation circuit 7 .
- the discharged vapor-phase refrigerant is guided to the outdoor heat exchanger 4 functioning as a condenser (radiator) through the four-way valve 3 .
- the vapor-phase refrigerant guided to the outdoor heat exchanger 4 is condensed by heat exchange with the air (outside air) sucked by the outdoor air blower 40 and is changed into a high-pressure liquid-phase refrigerant.
- the high-pressure liquid-phase refrigerant is decompressed in the process of passing through the expanding device 5 and is changed into a low-pressure vapor-liquid two-phase refrigerant.
- the vapor-liquid two-phase refrigerant is guided to the indoor heat exchanger 6 functioning as an evaporator (heat absorber, heat sink) and carries out heat exchange with the air (inside air) sucked by the indoor air blower 60 in the process of passing through the indoor heat exchanger 6 .
- the vapor-liquid two-phase refrigerant draws heat from the air to thereby evaporate and change into a low-temperature/low-pressure vapor-phase refrigerant.
- the air passing through the indoor heat exchanger 6 is cooled by the evaporative latent heat of the liquid-phase refrigerant and is sent to the place to be air-conditioned (cooled) by the indoor air blower 60 as a cool wind.
- the low-temperature/low-pressure vapor-phase refrigerant passing through the indoor heat exchanger 6 is guided to the accumulator 8 through the four-way valve 3 .
- the refrigerant When a liquid-phase refrigerant not fully evaporated is mixed into the refrigerant, the refrigerant is separated into the liquid-phase refrigerant and vapor-phase refrigerant at this place.
- the low-temperature/low-pressure vapor-phase refrigerant separated from the liquid-phase refrigerant is sucked into the compressor 2 from the accumulator 8 and is compressed again by the compressor 2 into a high-temperature/high-pressure vapor-phase refrigerant and is discharged into the circulation circuit 7 .
- the four-way valve 3 is switched in such a manner that the first port 3 a communicates with the third port 3 c , and second port 3 b communicates with the fourth port 3 d .
- the high-temperature/high-pressure vapor-phase refrigerant discharged from the compressor 2 is guided to the indoor heat exchanger 6 through the four-way valve 3 and is made to carry out heat exchange with the air passing through the indoor heat exchanger 6 .
- the indoor heat exchanger 6 functions as a condenser.
- the vapor-phase refrigerant passing through the indoor heat exchanger 6 condenses by carrying out heat exchange with the air (inside air) sucked by the indoor air blower 60 and changes into a high-pressure liquid-phase refrigerant.
- the air passing through the indoor heat exchanger 6 is heated by heat exchange with the vapor-phase refrigerant and is sent to the place to be air-conditioned (heated) by the indoor air blower 60 as a warm wind.
- the high-temperature liquid-phase refrigerant passing through the indoor heat exchanger 6 is guided to the expanding device 5 and is decompressed in the process of passing through the expanding device 5 and is further changed into a low-pressure vapor-liquid two-phase refrigerant.
- the vapor-liquid two-phase refrigerant is guided to the outdoor heat exchanger 4 functioning as an evaporator and carries out heat exchange with the air (outside air) sucked by the outdoor air blower 40 to thereby evaporate and change into a low-temperature/low-pressure vapor-phase refrigerant.
- the low-temperature/low-pressure vapor-phase refrigerant passing through the outdoor heat exchanger 4 is sucked into the compressor 2 through the four-way valve 3 and accumulator 8 and is compressed again by the compressor 2 into a high-temperature/high-pressure vapor-phase refrigerant and is discharged into the circulation circuit 7 .
- the air conditioner 1 is made operable in both the cooling mode and heating mode, the air conditioner 1 may also be a cooling-dedicated device or heating-dedicated device operable in only one of, for example, the cooling mode and heating mode.
- FIG. 2 is a vertical cross-sectional view of the compressor 2 .
- the compressor 2 is a so-called vertical rotary compressor and includes, as main components, an airtight container 10 , compression-mechanism unit 11 , and electric-motor unit 12 .
- the airtight container 10 includes a circumferential wall 10 a having a cylindrical shape and stands vertical relatively to the installation surface.
- the installation surface is, for example, a bottom plate or the like of the outdoor unit.
- a discharge pipe 10 b is provided at the upper end of the airtight container 10 .
- the discharge pipe 10 b is connected to the first port 3 a of the four-way valve 3 through the circulation circuit 7 .
- an oil basin part 10 c storing therein the lubricating oil is provided.
- the compression-mechanism unit 11 is accommodated in the airtight container 10 at the lower part thereof in such a manner as to be immersed in the lubricating oil.
- the compression-mechanism unit 11 has a twin-type cylinder structure and includes a first cylinder 13 , second cylinder 14 , and rotating shaft 15 as main components.
- Each of the first cylinder 13 and second cylinder 14 includes a roller (rolling piston) and vane inside thereof. It should be noted that the number of the cylinders of the compression-mechanism unit is not limited two, and may be one, or greater than or equal to three.
- the first cylinder 13 is fixed to the inner circumferential surface of the circumferential wall 10 a of the airtight container 10 .
- the second cylinder 14 is fixed to the undersurface of the first cylinder 13 through a partition plate 18 .
- a first bearing 20 is fixed to the upper part of the first cylinder 13 .
- the first bearing 20 covers the bore part of the first cylinder 13 from above and upwardly protrudes from the first cylinder 13 .
- the space surrounded by the bore part of the first cylinder 13 , partition plate 18 , and first bearing 20 constitutes a first cylinder chamber.
- the partition plate 18 and first bearing 20 respectively correspond to closure members defining the undersurface of the first cylinder chamber and top surface of the first cylinder chamber.
- a second bearing 22 is fixed to the lower part of the second cylinder 14 .
- the second bearing 22 covers the bore part of the second cylinder 14 from below and downwardly protrudes from the second cylinder 14 .
- the space surrounded by the bore part of the second cylinder 14 , partition plate 18 , and second bearing 22 constitutes a second cylinder chamber.
- the partition plate 18 and second bearing 22 respectively correspond to closure members defining the top surface of the second cylinder chamber and undersurface of the second cylinder chamber.
- the first cylinder chamber and second cylinder chamber are arranged concentrically with the central axis line O 1 of the airtight container 10 .
- the first cylinder chamber and second cylinder chamber are connected to the accumulator 8 through a suction pipe (illustration omitted) serving as a part of the circulation circuit 7 .
- the vapor-phase refrigerant separated from the liquid-phase refrigerant by the accumulator 8 is guided to the first cylinder chamber and second cylinder chamber through the aforementioned suction pipe.
- the rotating shaft 15 is positioned in such a manner that the central axis thereof is concentric with the central axis line O 1 of the airtight container 10 , and penetrates the first cylinder chamber, second cylinder chamber, and partition plate 18 .
- the rotating shaft 15 includes a first journal part 27 a , second journal part 27 b , and a pair of crankpin parts (eccentric parts) 28 a and 28 b . That is, the rotating shaft 15 is configured as a crankshaft.
- the first journal part 27 a is rotatably supported by the first bearing 20 .
- the second journal part 27 b is rotatably supported by the second bearing 22 .
- the rotating shaft 15 includes an extension part 27 c concentrically extended from the first journal part 27 a .
- the extension part 27 c penetrates the first bearing 20 to upwardly protrude from the compression-mechanism unit 11 .
- a rotor 33 (to be described later) of the electric-motor unit 12 is firmly fixed.
- the eccentric parts 28 a and 28 b are positioned between the first journal part 27 a and second journal part 27 b .
- the eccentric parts 28 a and 28 b respectively have phase differences of, for example, 180° and amounts of eccentricity of the eccentric parts 28 a and 28 b relative to the central axis line O 1 of the airtight container 10 are made equal to each other.
- the eccentric part (hereinafter referred to as a first eccentric part) 28 a on one hand is accommodated in the first cylinder chamber.
- the eccentric part (hereinafter referred to as a second eccentric part) 28 b on the other hand is accommodated in the second cylinder chamber.
- Rollers 16 and 17 are respectively fitted onto the outer circumferential surfaces of the first eccentric part 28 a and second eccentric part 28 b . Between the inner circumferential surface of each of the rollers 16 and 17 and outer circumferential surface of each of the eccentric parts 28 a and 28 b , a small gap allowing each of the rollers 16 and 17 to rotate relatively to each of the eccentric parts 28 a and 28 b is provided. Thereby, when the rotating shaft 15 rotates, each of the rollers 16 and 17 eccentrically rotates inside the cylinder chamber and part of the outer circumferential surface of each of the rollers 16 and 17 comes into contact with the inner circumferential surface of the cylinder chamber through an oil film.
- each of the vanes is supported by each of the cylinders 13 and 14 in a state where each of the vanes is inwardly impelled in the radial direction by impelling means.
- the tip end part of each of the vanes is slidably pressed against the outer circumferential surface of each of the rollers 16 and 17 .
- Each of these vanes is configured in such a manner as to partition the cylinder chamber of each of the cylinders 13 and 14 into a suction chamber and compression chamber in cooperation with each of the rollers 16 and 17 and move (advance/retreat) in the direction of protrusion into the cylinder chamber and direction of retreat from the cylinder chamber concomitantly with the eccentric rotation of each of the rollers 16 and 17 .
- Each of the vanes advances/retreats into/from the cylinder chamber as described above, whereby the capacity of each of the suction chamber and compression chamber of the cylinder chamber is changed, and vapor-phase refrigerant sucked into the cylinder chamber from the aforementioned suction pipe is compressed.
- the high-temperature/high-pressure vapor-phase refrigerant compressed in each of the cylinder chambers of the first cylinder 13 and second cylinder 14 is discharged into the inside of the airtight container 10 through each of discharge valve mechanisms 21 and 23 to be described later.
- the discharged vapor-phase refrigerant ascends inside the airtight container 10 .
- the lubricating oil stored in the oil basin part 10 c of the airtight container 10 is stirred.
- the stirred lubricating oil is changed into a mist-like form and ascends inside the airtight container 10 toward the discharge pipe 10 b under the favor of the flow of the vapor-phase refrigerant.
- an oil separator or the like configured to separate the lubricating oil contained in the vapor-phase refrigerant ascending inside the container 10 from the refrigerant is provided.
- the electric-motor unit 12 is accommodated in the airtight container 10 at an intermediate part along the central axis line O 1 of the airtight container 10 in such a manner as to be positioned between the compression-mechanism unit 11 and discharge pipe 10 b .
- the electric-motor unit 12 includes a so-called inner-rotor type motor and includes a rotor 33 firmly fixed to the rotating shaft 15 and stator 34 fixed to the inner circumferential surface of the circumferential wall 10 a of the airtight container 10 .
- a voltage is applied to the electric-motor unit 12 from the power source, whereby the rotor 33 is rotated around the central axis line O 1 relatively to the stator 34 and rotating shaft 15 is rotated together with the rotor 33 .
- the rotating shaft 15 is rotatably supported by the two bearings 20 and 22 .
- One of the two bearings 20 and 22 is a main bearing (hereinafter referred to as a first bearing) 20 and the other is an auxiliary bearing (hereinafter referred to as a second bearing) 22 .
- Each of the first bearing 20 and second bearing 22 rotatably supports the rotating shaft 15 .
- the first bearing 20 defines the top surface of the first cylinder chamber in the first cylinder 13 and second bearing 22 defines the undersurface of the second cylinder chamber in the second cylinder 14 .
- the top surface is an end face of each of the cylinders 13 and 14 on one end side thereof in the axial direction (direction along the central axis line O 1 of the airtight container 10 ) of the rotating shaft 15
- undersurface is an end face of each of the cylinders 13 and 14 on the other end side thereof in the aforementioned axial direction.
- the first bearing 20 corresponds to a member blocking the first cylinder chamber from above
- second bearing 22 corresponds to a member blocking the second cylinder chamber from below.
- the first bearing 20 includes a first flange part 20 a defining the top surface of the first cylinder chamber in the first cylinder 13 and first boss part 20 b upwardly extending in a cylindrical form so as to be continuous with the first flange part 20 a .
- the first flange part 20 a is positioned at the lower end of the first boss part 20 b , extends toward the outside of the first boss part 20 b in the radial direction thereof, and is continuous throughout the entire circumference of a circular shape concentric with the central axis of the rotating shaft 15 .
- a discharge hole hereinafter referred to as a first discharge hole
- the first discharge hole 20 c penetrates a part of the first flange part 20 a in the vertical direction and communicates with the inside of the compression chamber of the first cylinder 13 .
- the first discharge hole 20 c is opened/closed by a predetermined valve mechanism (hereinafter referred to as a first discharge valve mechanism) 21 .
- the first discharge valve mechanism 21 is arranged in the first flange part 20 a , opens the first discharge hole 20 c concomitantly with an increase in the pressure inside the compression chamber of the first cylinder 13 to thereby discharge the high-temperature/high-pressure vapor-phase refrigerant from the compression chamber.
- the first boss part 20 b is a part into which the rotating shaft 15 , more specifically, the first journal part 27 a is inserted at the first bearing 20 , and which rotatably supports the first journal part 27 a .
- the first boss part 20 b is arranged so as to be concentric with the rotating shaft 15 . That is, the first boss part 20 b is arranged perpendicular to the first flange part 20 a . In the state where the first journal part 27 a is inserted into the first boss part 20 b , the outer circumferential surface thereof is slid along the inner circumferential surface of the first boss part 20 .
- the second bearing 22 includes a second flange part 22 a defining the undersurface of the second cylinder chamber in the second cylinder 14 and second boss part 22 b downwardly extending in a cylindrical form so as to be continuous with the second flange part 22 a.
- the second flange part 22 a is positioned at the upper end of the second boss part 22 b , extends toward the outside of the second boss part 22 b in the radial direction thereof, and is continuous throughout the entire circumference of a circular shape concentric with the central axis of the rotating shaft 15 .
- a discharge hole (illustration omitted, hereinafter referred to as a second discharge hole) through which the refrigerant is discharged from the compression chamber of the second cylinder 14 is formed.
- the second discharge hole penetrates a part of the second flange part 22 a in the vertical direction and communicates with the inside of the compression chamber of the second cylinder 14 .
- the second discharge hole is opened/closed by a predetermined valve mechanism (hereinafter referred to as a second discharge valve mechanism) 23 .
- the second discharge valve mechanism 23 opens the second discharge hole concomitantly with an increase in the pressure inside the compression chamber of the second cylinder 14 to thereby discharge the high-temperature/high-pressure vapor-phase refrigerant from the compression chamber.
- the second boss part 22 b is a part into which the rotating shaft 15 , more specifically, the second journal part 27 b is inserted at the second bearing 22 , and which rotatably supports the second journal part 27 b .
- the second boss part 22 b is arranged so as to be concentric with the rotating shaft 15 . That is, the second boss part 22 b is arranged perpendicular to the second flange part 22 a . In the state where the second journal part 27 b is inserted into the second boss part 22 b , the outer circumferential surface thereof is slid along the inner circumferential surface of the second boss part 22 b.
- FIG. 3 is a view schematically showing the first bearing 20 including the first discharge valve mechanism 21 from above.
- FIG. 4 is a cross-sectional view schematically showing the first bearing 20 at the part indicated by the arrows A 3 shown in FIG. 3 .
- the configurations of the first discharge valve mechanism 21 and second discharge valve mechanism 23 are approximately equal to each other except for the fact that there is a point of difference incidental to the fact that the mechanism 21 and mechanism 23 are positioned opposite to each other in the vertical direction. Accordingly, the configuration of the second discharge valve mechanism 23 conforms to the configuration shown in FIG. 3 and FIG. 4 . Accordingly, hereinafter the configuration example of the first discharge valve mechanism 21 will be described.
- the first discharge valve mechanism 21 is provided in the first flange part 20 a of the first bearing 20 , appropriately opens the first discharge hole 20 c to thereby discharge the refrigerant compressed in the compression chamber of the first cylinder 13 from the compression chamber.
- the first discharge valve mechanism 21 includes a discharge valve 21 a and valve presser 21 b .
- the discharge valve 21 a and valve presser 21 b are fixed to the first flange part 20 a with a predetermined fixing member 21 c .
- the fixing member 21 c an arbitrary fixing member, for example, a bolt, screw, rivet or the like is applied.
- the first discharge hole 20 c is opened at the bottom of a concave part (hereinafter referred to as a dug-down part) 20 d formed in the first flange part 20 a .
- the dug-down part 20 d is formed by making the top surface (end face on one end side in the axial direction of the rotating shaft 15 ) of the first flange part 20 a concave to a predetermined depth.
- the depth of the dug-down part 20 d is made approximately equal to the dimension of the first discharge valve mechanism 21 (valve presser 21 b laid on top of discharge valve 21 a ) in the vertical direction.
- the contour of the dug-down part 20 d viewed from above the first flange part 20 a is made a similar figure of the contour slightly greater than the aforementioned contour of the first discharge valve mechanism 21 viewed from above the first flange part 20 a so that the first discharge valve mechanism 21 (discharge valve 21 a and valve presser 21 b ) can be installed inside the dug-down part 20 d . That is, the longitudinal direction of the dug-down part 20 d is parallel to the longitudinal direction of the discharge valve 21 a and valve presser 21 b to be described later.
- the dug-down part 20 d By making the dug-down part 20 d have such a configuration, when the first discharge valve mechanism 21 is installed inside the dug-down part 20 d , the mechanism 21 is in a state where the mechanism 21 is fully hidden in the dug-down part 20 d .
- the dug-down part 20 d is formed in the first flange part 20 a as a concave part in which the first discharge valve mechanism 21 is to be installed.
- a dug-down part 22 d (see FIG. 2 ) identical to the dug-down part 20 d is formed as a concave part in which the second discharge valve mechanism 23 is to be installed.
- the discharge valve 21 a is a member configured to close or open the first discharge hole 20 c , and has a plate-like shape lengthwise in the predetermined direction.
- the discharge valve 21 a is formed of a material capable of elastic deformation such as spring steel or the like into an oblong card-like shape.
- the discharge valve 21 a is made to have a cantilever leaf spring structure capable of flexure deformation in the state where one end thereof in the longitudinal direction fixed by a fixing member 21 c is made the fixed end, and the other end thereof in the longitudinal direction is made the free end.
- the discharge valve 21 a undergoes deformation and opens the first discharge hole 20 c .
- this state of the discharge valve 21 a is referred to as the deformed state.
- the discharge valve 21 a is in pressure contact with the circumferential edge of the first discharge hole 20 c in such a manner as to block up the first discharge hole 20 c by an elastic force (pressing force) less than the aforementioned predetermined discharge pressure.
- the discharge pressure deforms the discharge valve 21 a against the elastic force (pressing force) thereof to thereby make the discharge valve 21 a open the first discharge hole 20 c and discharge the refrigerant.
- the discharge valve 21 a is elastically restored from the deformed state to the normal state and blocks up the first discharge hole 20 c again.
- the valve presser 21 b is a member configured to restrain the discharge valve 21 a from deformation, and has a plate-like shape lengthwise in the predetermined direction and having a thickness greater than the discharge valve 21 a .
- the valve presser 21 b is formed of, for example, a steel material or the like.
- the valve presser 21 b is arranged in such a manner that the longitudinal direction thereof is made along the longitudinal direction of the discharge valve 21 a .
- These longitudinal directions are directions intersecting the radial direction of the first flange part 20 a , in other words, the directions intersecting a plane including the central axis of the rotating shaft 15 . Further, these longitudinal directions are parallel to the longitudinal direction of the dug-down part 20 d . In the example shown in FIG.
- the aforementioned longitudinal direction is the direction orthogonal to the radial direction of the first flange part 20 a , in other words, the direction orthogonal to the plane including the central axis of the rotating shaft 15 .
- the valve presser 21 b is arranged in such a manner as to be opposed to the discharge valve 21 a in the process in which when opening the first discharge hole 20 c , the discharge valve 21 a makes a displacement to a position separate from the first discharge hole 20 c .
- the valve presser 21 b is arranged above the discharge valve 21 a in such a manner as to cover the discharge valve 21 a .
- the valve presser 21 b exhibits a bent (slightly levitated) state for opening the first discharge hole 20 c , i.e., a retroflex configuration conforming to the posture of the discharge valve 21 a in the deformed state.
- the valve presser 21 b gets contact with the deformed discharge valve 21 a to thereby prevent the discharge valve 21 a from undergoing further deformation (levitation).
- a muffler 41 configured to cover the first bearing 20 is provided.
- the first muffler 41 suppresses pulsation and noise caused by, for example, the refrigerant to be discharged from the compression chamber of the first cylinder 13 into the inside of the airtight container 10 .
- the first muffler 41 covers the first bearing 20 so as to surround the part between the first flange part 20 a and first boss part 20 b , and forms a first muffler chamber 43 between the first flange part 20 a and first boss part 20 b .
- the first muffler chamber 43 is a space into which the high-temperature/high-pressure refrigerant compressed in the compression chamber of the first cylinder 13 is discharge from the first discharge hole 20 c in the first place.
- the first muffler 41 includes communicating holes 41 a configured to make the inside and outside (space above and below the first muffler wall) of the first muffler 41 communicate with each other.
- the high-temperature/high-pressure vapor-phase refrigerant discharged into the first muffler chamber 43 through the first discharge hole 20 c is discharged into the inside of the airtight container 10 through the communicating holes 41 a.
- a muffler (hereinafter referred to as a second muffler) 42 configured to cover the second bearing 22 is provided.
- the second muffler 42 suppresses pulsation and noise caused by, for example, the refrigerant to be discharged from the compression chamber of the second cylinder 14 into the inside of the airtight container 10 .
- the second muffler 42 covers the second bearing 22 so as to surround the part between the second flange part 22 a and second boss part 22 b , and forms a second muffler chamber 44 between the second flange part 22 a and second boss part 22 b .
- the second muffler chamber 44 is a space into which the high-temperature/high-pressure refrigerant compressed in the compression chamber of the second cylinder 14 is discharge from the second discharge hole in the first place.
- the second muffler chamber 44 communicates with the first muffler chamber 43 through a communicating hole provided in the compression-mechanism unit 11 .
- the communicating hole penetrates each of the second flange part 22 a , second cylinder 14 , partition plate 18 , first cylinder 13 , and first flange part 20 a and is opened to the second muffler chamber 44 and first muffler chamber 43 .
- the high-temperature/high-pressure vapor-phase refrigerant discharged into the second muffler chamber 44 through the second discharge hole reaches the first muffler chamber 43 through the aforementioned communicating hole and is thereafter discharged into the inside of the airtight container 10 through the communicating holes 41 a.
- FIG. 5 is a view schematically showing, from above, the state where the first muffler 41 is mounted on the first bearing 20 .
- FIG. 6 is a perspective view schematically showing the first muffler 41 .
- the first muffler 41 is a three-dimensional component including an end face part 45 , side face part 46 , and brim part 47 , and these three parts are formed so as to have a thin-walled structure.
- the end face part 45 , side face part 46 , and brim part 47 define the outer contour of the first muffler chamber 43 .
- the end face part 45 is a face part of the first muffler 41 on one end side thereof in the axial direction (direction along the central axis line O 1 of the airtight container 10 ) of the rotating shaft 15 and is a face part radially spreading relatively to the central axis of the rotating shaft 15 .
- the end face part 45 corresponds to the top face part of the first muffler 41 .
- the end face part 45 has an annular shape including a circular opening 45 a in which the first boss part 20 b of the first bearing 20 is to be inserted.
- the center of the opening 45 a is positioned on the central axis (central axis line O 1 of the airtight container 10 ) of the rotating shaft 15 .
- the first muffler 41 is arranged in such a manner that the opening 45 a is concentric with the rotating shaft 15 .
- the bore diameter (distance across the opening) of the opening 45 a is made approximately equal to the dimension of the outer diameter of the first boss part 20 b at the insertion portion.
- the end face part 45 includes five piece parts 45 b to 45 f radially extending relatively to the center of the opening 45 a .
- the five piece parts 45 b to 45 f are arranged at approximately regular intervals in the circumferential direction of the opening 45 a .
- the five piece parts 45 b to 45 f are, except for the part between the piece part 45 b and piece part 45 f , gently continuous with each other in such a manner that adjacent piece parts gradually become closer to the centerline (central axis line O 1 of the airtight container 10 ) of the opening 45 a .
- each of the four piece parts 45 c to 45 f includes a communicating hole 41 a formed therein. It should be noted that the number of the piece parts included in the end face part is not limited to five, and may less than or equal to four, or may be greater than or equal to six.
- the side face part 46 joins the end face part 45 (specifically, five piece parts 45 b to 45 f ) and brim part 47 to each other in a cylindrical form throughout the entire circumference in the circumferential direction of the opening 45 a , in other words, the central axis of the rotating shaft 15 .
- the side face part 46 corresponds to the outer circumferential part of the first muffler 41 .
- the part on the upper side thereof continuous with the end face part 45 has a cylindrical shape thinner than the part on the lower side thereof continuous with the brim part 47 .
- the side face part 46 is inclined in such a manner that the greater the distance from one side thereof continuous with the brim part 47 toward the other side thereof continuous with the end face part 45 , the closer to the centerline (central axis line O 1 of the airtight container 10 ) of the opening 45 a the side face part 46 becomes.
- the brim part 47 is a face part of the first muffler 41 on the other end side thereof in the axial direction (direction along the central axis line O 1 of the airtight container 10 ) of the rotating shaft 15 , and is a face part spreading approximately in parallel with the end face part 45 in a circular form concentric with the central axis of the rotating shaft 15 .
- the brim part 47 corresponds to the undersurface part of the first muffler 41 , and is continuous with the side face part 46 at a part of the first muffler 41 on the lower end side thereof.
- the brim part 47 includes through-holes into which the bolts are to be inserted.
- the bolt is an example of a fixing member (in this embodiment, a second fixing member used to fix the first muffler 41 ) configured to fix the first muffler 41 to the first flange part 20 a .
- the brim part 47 includes five through-holes 47 a to 47 e . Into each of these through-holes 47 a to 47 e , one bolt is inserted and, in total five bolts 48 a to 48 e are inserted into these through-holes 47 a to 47 e . These through-holes 47 a to 47 e are arranged alongside at approximately regular intervals in the circumferential direction of the opening 45 a .
- the five through-holes 47 a to 47 e are arranged in such a manner that the each of the through-holes 47 a to 47 e is positioned between piece parts 45 b to 45 f adjacent to each other at the end face part 45 .
- the five through-holes 47 a to 47 e and five piece parts 45 b to 45 f are arranged in such a manner that the through-holes 47 a to 47 e and piece parts 45 b to 45 f are alternately positioned in the circumferential direction of the opening 45 a with approximately equal phase angle differences held between the alternately arranged through-holes 47 a to 47 e and piece parts 45 b to 45 f .
- the number of the through-holes possessed by the brim part is not limited to five, and may be less than or equal to four, or greater than or equal to six. For example, it is sufficient if the number of the through-holes included in the brim part is made equal to the number of the piece parts included in the end face part.
- the through-holes 47 a to 47 e respectively communicate with the through-holes 20 f to 20 j formed in the first flange part 20 a of the first bearing 20 .
- the first through-hole 47 a communicates with the first through-hole 20 f .
- the bolt 48 a is inserted into these through-holes 47 a and 20 f communicating with each other.
- the second through-hole 47 b communicates with the second through-hole 20 g .
- the bolt 48 b is inserted.
- the third through-hole 47 c communicates with the third through-hole 20 h .
- the bolt 48 c is inserted into these through-holes 47 c and 20 h communicating with each other.
- the fourth through-hole 47 d communicates with the fourth through-hole 20 i .
- the bolt 48 d is inserted into these through-holes 47 d and 20 i communicating with each other.
- the fifth through-hole 47 e communicates with the fifth through-hole 20 j .
- the bolt 48 e is inserted into these through-holes 47 e and 20 j communicating with each other.
- These bolts 48 a to 48 e are each fastened to the first cylinder 13 . Thereby, the first muffler 41 and first bearing 20 are implemented on the first cylinder 13 .
- the brim part 47 is fixed to the first cylinder 13 through the first flange part 20 a of the first bearing 20 with the bolts 48 a to 48 e . That is, the bolts 48 a to 48 e fix the brim part 47 to the first cylinder 13 through the first flange part 20 a.
- the first muffler 41 includes a concave part 49 formed by inwardly denting a part of the portion defining the outer contour of the first muffler chamber 43 to be formed by the first muffler 41 toward the inside of the first muffler chamber 43 .
- the configuration of the concave part 49 will be described with reference to FIGS. 4 to 6 .
- the concave part 49 has a configuration formed by denting each of the end face part 45 and side face part 46 toward the inside of the first muffler chamber 43 .
- the concave part 49 is a convex part protruding into the first muffler chamber 43 and corresponds to a rib of the first muffler 41 . That is, the concave part 49 functions as a reinforcing part configured to suppress deformation of the first muffler 41 .
- the concave part 49 has the configuration formed by denting each of the portion between the piece part 45 b and piece part 45 f at the end face part 45 and portion connecting between the piece part 45 b , piece part 45 f , and brim part 47 at the side face part 46 toward the inside of the first muffler chamber 43 .
- the concave part 49 When projected onto the top surface 20 e of the first flange part 20 a from the axial direction of the rotating shaft 15 , the concave part 49 is arranged in such a manner as to intersect the longitudinal direction of the dug-down part 20 d and thereby overlap the dug-down part 20 d . That is, the concave part 49 is arranged in the vicinity of the dug-down part 20 d , in other words, in the vicinity of the discharge valve 21 a and valve presser 21 b.
- the concave part 49 is configured to include four face parts 49 a to 49 d as the main face parts.
- the first face part 49 a and second face part 49 b are opposed to each other as a pair approximately in parallel with each other in the circumferential direction of the opening 45 a . Further, the first face part 49 a and second face part 49 b are parallel to a predetermined plane (virtual plane) including the central axis of the rotating shaft 15 and intersecting the longitudinal direction of the discharge valve 21 a.
- the first face part 49 a and second face part 49 b are parallel to the plane including the central axis of the rotating shaft 15 and orthogonal to the longitudinal direction of the discharge valve 21 a .
- the first face part 49 a and second face part 49 b are arranged in such a manner as to intersect the longitudinal direction of the dug-down part 20 d , i.e., in this case, as to intersect the longitudinal direction of the dug-down part 20 d at right angles and thereby overlap the dug-down part 20 d , i.e., the discharge valve 21 a and valve presser 21 b.
- the third face part 49 c and fourth face part 49 d are face parts continuous with each other and connecting between the first face part 49 a and second face part 49 b .
- the first face part 49 a and second face part 49 b are continuous with each other through the third face part 49 c and fourth face part 49 d .
- the third face part 49 c rises approximately in parallel with the centerline (central axis line O 1 of the airtight container 10 ) of the opening 45 a , and connects between the first face part 49 a and second face part 49 b at the upper part thereof.
- the fourth face part 49 d rises so as to be inclined toward the centerline (central axis line O 1 of the airtight container 10 ) of the opening 45 a , and connects between the first face part 49 a and second face part 49 b at the lower part thereof.
- the fourth face part 49 d is inclined in such a manner that the closer to one side (in this case, upper side) thereof continuous with the third face part 49 c , the closer to the centerline (central axis line O 1 of the airtight container 10 ) of the opening 45 a becomes the fourth face part 49 d .
- the third face part 49 c and fourth face part 49 d are perpendicularly continuous with the first face part 49 a and second face part 49 b.
- the third face part 49 c includes a through-hole 49 e into which a bolt 50 is to be inserted.
- the bolt 50 is an example of a fixing member (in this embodiment, a first fixing member configured to fix the first muffler 41 ) configured to fix the first muffler 41 , specifically, the side face part 46 to the first boss part 20 b .
- a seating face part 20 k including a flat seating face capable of coming into contact with the third face part 49 c is provided on the first boss part 20 b .
- the bolt 50 is fastened to a bolt-hole 201 formed in the seating face part 20 k .
- the first face part 49 a and second face part 49 b are in opposition to each other with a separation distance (clearance) for prevention of interference with the head 50 a of the bolt 50 held between the face parts 49 a and 49 b.
- the first muffler 41 is fixed to the first cylinder 13 is fixed to the first bearing 20 , i.e., to the first cylinder 13 through the first flange part 20 a with the bolts 48 a to 48 e , and is fixed to the first boss part 20 b with the bolt 50 .
- the first flange part 20 a is arranged in such a manner as to outwardly extend in the radial direction of the rotating shaft 15
- first boss part 20 b is arranged concentric with the rotating shaft 15 . That is, the first flange part 20 a and first boss part 20 b are arranged orthogonal to each other.
- the first muffler 41 it is possible to firmly fix the first muffler 41 to the first bearing 20 in two directions, i.e., in the radial direction and axial direction of the rotating shaft 15 . Thereby, it is possible to enhance the stiffness of the first muffler 41 against, for example, the inclination of the first boss part 20 b at the time of rotation of the rotating shaft 15 .
- the first muffler 41 includes the concave part 49 arranged in the vicinity of the dug-down part 20 d of the first flange part 20 a .
- the concave part 49 functions as a reinforcing part configured to suppress deformation of the first muffler 41 . Accordingly, it is possible for the concave part 49 , when the rotating shaft 15 is rotated, to bear the burden of the force attempting to make the dug-down part 20 d undergo elastic deformation so as to incline the first boss part 20 b toward, for example, the first flange part 20 a .
- the second muffler 42 includes no part corresponding to the concave part 49 possessed by the aforementioned first muffler 41 .
- the length of the rotating shaft 15 in the axial direction thereof is less than the first boss part 20 b of the first bearing 20 . That is, such a deformation as to incline the second boss part 22 b toward the second flange part 22 a hardly occurs to the second boss part 22 b and, even when deformed, the second boss part 22 b is not so largely deformed as the first boss part 20 b .
- the second muffler 42 has the configuration in which the part corresponding to the concave part 49 is omitted. That is, the second muffler 42 can be configured in the same manner as the first muffler 41 except for the differences incidental to the point that the second muffler 42 has no part corresponding to the concave part 49 and point that the second muffler 42 is positioned opposite (upside down) in the vertical direction to the first muffler 41 . However, the second muffler 42 may have a concave part identical to the first muffler 41 .
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Abstract
Description
- This application is based upon and claims the benefit of priority from Japanese Patent Application No. 2021-140934, filed Aug. 31, 2021, the entire contents of which are incorporated herein by reference.
- Embodiments described herein relate generally to a compressor and air conditioner including the compressor.
- A refrigerating cycle device such as an air conditioner or the like is equipped with a compressor configured to compress the refrigerant. The compressor includes, as main components, for example, an electric-motor unit configured to rotate, for example, a rotating shaft, compression-mechanism unit coupled to the electric-motor unit through the rotating shaft, and airtight container accommodating therein the electric-motor unit and compression-mechanism unit. The electric-motor unit includes, for example, a so-called inner-rotor type motor and includes a rotor firmly fixed to the rotating shaft and stator fixed to the inner circumferential part of the airtight container. The rotating shaft includes crank parts (eccentric parts). The compression-mechanism unit includes cylinders each forming, for example, cylinder chambers, and rollers fitted onto the eccentric parts of the rotating shaft and eccentrically rotated inside the cylinder chambers. The inside of the cylinder chamber is partitioned into a suction chamber and compression chamber of the refrigerant with a vane. The rotating shaft is rotatably supported with bearings. The bearing includes a flange part defining a surface in the cylinder chamber in the axial direction of the rotating shaft, and boss part extending in a cylindrical form from the flange part. Further, a muffler configured to suppress pulsation and noise caused by the refrigerant to be compressed by the cylinder of the compression-mechanism unit and discharged into the airtight container is attached to the bearing.
- The flange part includes a discharge port from which the refrigerant compressed by the cylinder is discharged into the airtight container, and discharge valve mechanism configured to control opening/closing of the discharge port. For this reason, the flange part includes a concave part (dug-down part) in which the discharge valve mechanism is to be installed in the vicinity of the discharge port. The dug-down part is formed by digging down one surface in the bearing in the axial direction of the rotating shaft, for example, the top surface of the flange part to a predetermined depth. Accordingly, the dug-down part has a less thickness as compared with other portions of the flange part, and the rigidity thereof is liable to become relatively lower in the bearing. Accordingly, when the rotating shaft is rotated, there is a possibility of the dug-down part being elastically deformed in such a manner as to incline the boss part toward, for example, the flange part. Depending on the degree of such a deformation of the dug-down part, there is a possibility of the support rigidity of the rotating shaft based on the bearings being lowered, and possibility of the rotating shaft causing bending vibration and enhancing the noise.
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FIG. 1 is a circuit diagram schematically showing the configuration of an air conditioner according to an embodiment. -
FIG. 2 is a vertical cross-sectional view of a compressor according to the embodiment. -
FIG. 3 is a view schematically showing a bearing (first bearing including a first discharge valve mechanism) including a discharge valve mechanism of the compressor according to the embodiment from above. -
FIG. 4 is a view schematically showing the cross section of the bearing (first bearing) at the part indicated by the arrows A3 shown inFIG. 3 . -
FIG. 5 is a view schematically showing, from above, the state where a muffler (first muffler) of the compressor according to the embodiment is mounted on the bearing (first bearing). -
FIG. 6 is a perspective view schematically showing the muffler (first muffler) of the compressor according to the embodiment. - In general, according to one embodiment, a compressor comprises cylinders, a rotating shaft, bearings, at least one of discharge valve mechanisms, and at least one of mufflers. The cylinders compress a refrigerant. A rotating shaft arranges inside the cylinders and includes eccentric parts. Each of the bearings includes a flange part defining a surface in the cylinder in an axial direction of the rotating shaft, and a boss part extending in a cylindrical form concentric with the rotating shaft so as to be continuous with the flange part and rotatably supporting the rotating shaft. At least one of the discharge valve mechanisms is arranged in the flange part and includes a discharge valve deformed to be opened when the refrigerant compressed by the cylinder reaches a predetermined discharge pressure and lengthwise in a predetermined direction, and a valve presser suppressing further deformation of the discharge valve when the discharge valve is opened. At least one of the mufflers covers the bearing so as to surround a part between the flange part and the boss part and forms, between the flange part and the boss part, a muffler chamber into which the refrigerant compressed by the cylinder is discharged. As to the mufflers, an outer contour of the muffler chamber is defined by each of an end face part which is a face part on one end side of the muffler in the axial direction of the rotating shaft, a brim part which is a face part on the other end side in the axial direction of the rotating shaft, and a side face part which joins the end face part and the brim part to each other in a cylindrical form throughout the entire circumference in the circumferential direction of the rotating shaft, and at least one of the mufflers includes a concave part formed by denting each of the end face part and the side face part toward the inside of the muffler chamber.
- An embodiment will be described hereinafter with reference to
FIGS. 1 to 6 . -
FIG. 1 is a refrigerating cycle circuit diagram of an air conditioner 1 according to this embodiment. The air conditioner 1 is a device configured to carry out air conditioning on the basis of such a refrigerating cycle and is an example of the refrigerating cycle device. The air conditioner 1 includes, as main components, acompressor 2, four-way valve 3, outdoor heat exchanger 4, outdoor heat exchanger 4,outdoor air blower 40, expanding device 5, indoor heat exchanger 6, andindoor air blower 60. - As shown in
FIG. 1 , the discharge side of thecompressor 2 is connected to afirst port 3 a of the four-way valve 3. Asecond port 3 b of the four-way valve 3 is connected to the outdoor heat exchanger 4. The outdoor heat exchanger 4 is connected to the indoor heat exchanger 6 through the expanding device 5. The indoor heat exchanger 6 is connected to athird port 3 c of the four-way valve 3. Afourth port 3 d of the four-way valve 3 is connected to the suction side of thecompressor 2 through an accumulator 8. - The refrigerant circulates through a
circulation circuit 7 from the discharge side of thecompressor 2 to the suction side thereof through the outdoor heat exchanger 4, expanding device 5, indoor heat exchanger 6, and accumulator 8. As the refrigerant, a refrigerant containing no chlorine is desirable and, for example, R448A, R449A, R449B, R407G, R407H, R449C, R456A, R516A, R406B, R463A, R744, and HC-based refrigerant and the like are applicable. - For example, when the air conditioner 1 is operated in the cooling mode, the four-
way valve 3 is switched in such a manner that thefirst port 3 a communicates with thesecond port 3 b, andthird port 3 c communicates with thefourth port 3 d. When the operation of the air conditioner 1 is started in the cooling mode, the high-temperature/high-pressure vapor-phase refrigerant compressed by thecompressor 2 is discharged into thecirculation circuit 7. The discharged vapor-phase refrigerant is guided to the outdoor heat exchanger 4 functioning as a condenser (radiator) through the four-way valve 3. - The vapor-phase refrigerant guided to the outdoor heat exchanger 4 is condensed by heat exchange with the air (outside air) sucked by the
outdoor air blower 40 and is changed into a high-pressure liquid-phase refrigerant. The high-pressure liquid-phase refrigerant is decompressed in the process of passing through the expanding device 5 and is changed into a low-pressure vapor-liquid two-phase refrigerant. The vapor-liquid two-phase refrigerant is guided to the indoor heat exchanger 6 functioning as an evaporator (heat absorber, heat sink) and carries out heat exchange with the air (inside air) sucked by theindoor air blower 60 in the process of passing through the indoor heat exchanger 6. - As a result of this, the vapor-liquid two-phase refrigerant draws heat from the air to thereby evaporate and change into a low-temperature/low-pressure vapor-phase refrigerant. The air passing through the indoor heat exchanger 6 is cooled by the evaporative latent heat of the liquid-phase refrigerant and is sent to the place to be air-conditioned (cooled) by the
indoor air blower 60 as a cool wind. The low-temperature/low-pressure vapor-phase refrigerant passing through the indoor heat exchanger 6 is guided to the accumulator 8 through the four-way valve 3. When a liquid-phase refrigerant not fully evaporated is mixed into the refrigerant, the refrigerant is separated into the liquid-phase refrigerant and vapor-phase refrigerant at this place. The low-temperature/low-pressure vapor-phase refrigerant separated from the liquid-phase refrigerant is sucked into thecompressor 2 from the accumulator 8 and is compressed again by thecompressor 2 into a high-temperature/high-pressure vapor-phase refrigerant and is discharged into thecirculation circuit 7. On the other hand, when the air conditioner 1 is operated in the heating mode, the four-way valve 3 is switched in such a manner that thefirst port 3 a communicates with thethird port 3 c, andsecond port 3 b communicates with thefourth port 3 d. When the operation of the air conditioner 1 is started in the heating mode, the high-temperature/high-pressure vapor-phase refrigerant discharged from thecompressor 2 is guided to the indoor heat exchanger 6 through the four-way valve 3 and is made to carry out heat exchange with the air passing through the indoor heat exchanger 6. - In this case, the indoor heat exchanger 6 functions as a condenser.
- As a result of this, the vapor-phase refrigerant passing through the indoor heat exchanger 6 condenses by carrying out heat exchange with the air (inside air) sucked by the
indoor air blower 60 and changes into a high-pressure liquid-phase refrigerant. The air passing through the indoor heat exchanger 6 is heated by heat exchange with the vapor-phase refrigerant and is sent to the place to be air-conditioned (heated) by theindoor air blower 60 as a warm wind. - The high-temperature liquid-phase refrigerant passing through the indoor heat exchanger 6 is guided to the expanding device 5 and is decompressed in the process of passing through the expanding device 5 and is further changed into a low-pressure vapor-liquid two-phase refrigerant. The vapor-liquid two-phase refrigerant is guided to the outdoor heat exchanger 4 functioning as an evaporator and carries out heat exchange with the air (outside air) sucked by the
outdoor air blower 40 to thereby evaporate and change into a low-temperature/low-pressure vapor-phase refrigerant. The low-temperature/low-pressure vapor-phase refrigerant passing through the outdoor heat exchanger 4 is sucked into thecompressor 2 through the four-way valve 3 and accumulator 8 and is compressed again by thecompressor 2 into a high-temperature/high-pressure vapor-phase refrigerant and is discharged into thecirculation circuit 7. - It should be noted that although in this embodiment, the air conditioner 1 is made operable in both the cooling mode and heating mode, the air conditioner 1 may also be a cooling-dedicated device or heating-dedicated device operable in only one of, for example, the cooling mode and heating mode.
- Next, the specific configuration of the
compressor 2 to be used for the air conditioner 1 will be described below with reference toFIG. 2 .FIG. 2 is a vertical cross-sectional view of thecompressor 2. As shown inFIG. 2 , thecompressor 2 is a so-called vertical rotary compressor and includes, as main components, anairtight container 10, compression-mechanism unit 11, and electric-motor unit 12. It should be noted that in the following description, on the basis of the relative positional relationship between the compression-mechanism unit 11 and electric-motor unit 12 arranged along the central axis line C1 of theairtight container 10 to be described later, the side on which the compression-mechanism unit 11 is positioned is defined as below, and side on which the electric-motor unit 12 is positioned is defined as above. - The
airtight container 10 includes acircumferential wall 10 a having a cylindrical shape and stands vertical relatively to the installation surface. The installation surface is, for example, a bottom plate or the like of the outdoor unit. At the upper end of theairtight container 10, adischarge pipe 10 b is provided. Thedischarge pipe 10 b is connected to thefirst port 3 a of the four-way valve 3 through thecirculation circuit 7. At the lower part of theairtight container 10, anoil basin part 10 c storing therein the lubricating oil is provided. - The compression-
mechanism unit 11 is accommodated in theairtight container 10 at the lower part thereof in such a manner as to be immersed in the lubricating oil. In the example shown inFIG. 2 , the compression-mechanism unit 11 has a twin-type cylinder structure and includes afirst cylinder 13,second cylinder 14, androtating shaft 15 as main components. Each of thefirst cylinder 13 andsecond cylinder 14 includes a roller (rolling piston) and vane inside thereof. It should be noted that the number of the cylinders of the compression-mechanism unit is not limited two, and may be one, or greater than or equal to three. - The
first cylinder 13 is fixed to the inner circumferential surface of thecircumferential wall 10 a of theairtight container 10. Thesecond cylinder 14 is fixed to the undersurface of thefirst cylinder 13 through apartition plate 18. - To the upper part of the
first cylinder 13, afirst bearing 20 is fixed. Thefirst bearing 20 covers the bore part of thefirst cylinder 13 from above and upwardly protrudes from thefirst cylinder 13. The space surrounded by the bore part of thefirst cylinder 13,partition plate 18, andfirst bearing 20 constitutes a first cylinder chamber. Thepartition plate 18 andfirst bearing 20 respectively correspond to closure members defining the undersurface of the first cylinder chamber and top surface of the first cylinder chamber. - To the lower part of the
second cylinder 14, asecond bearing 22 is fixed. Thesecond bearing 22 covers the bore part of thesecond cylinder 14 from below and downwardly protrudes from thesecond cylinder 14. The space surrounded by the bore part of thesecond cylinder 14,partition plate 18, andsecond bearing 22 constitutes a second cylinder chamber. Thepartition plate 18 andsecond bearing 22 respectively correspond to closure members defining the top surface of the second cylinder chamber and undersurface of the second cylinder chamber. The first cylinder chamber and second cylinder chamber are arranged concentrically with the central axis line O1 of theairtight container 10. - The first cylinder chamber and second cylinder chamber are connected to the accumulator 8 through a suction pipe (illustration omitted) serving as a part of the
circulation circuit 7. The vapor-phase refrigerant separated from the liquid-phase refrigerant by the accumulator 8 is guided to the first cylinder chamber and second cylinder chamber through the aforementioned suction pipe. - The rotating
shaft 15 is positioned in such a manner that the central axis thereof is concentric with the central axis line O1 of theairtight container 10, and penetrates the first cylinder chamber, second cylinder chamber, andpartition plate 18. The rotatingshaft 15 includes afirst journal part 27 a,second journal part 27 b, and a pair of crankpin parts (eccentric parts) 28 a and 28 b. That is, the rotatingshaft 15 is configured as a crankshaft. Thefirst journal part 27 a is rotatably supported by thefirst bearing 20. Thesecond journal part 27 b is rotatably supported by thesecond bearing 22. - Furthermore, the rotating
shaft 15 includes anextension part 27 c concentrically extended from thefirst journal part 27 a. Theextension part 27 c penetrates thefirst bearing 20 to upwardly protrude from the compression-mechanism unit 11. To theextension part 27 c, a rotor 33 (to be described later) of the electric-motor unit 12 is firmly fixed. - The
eccentric parts first journal part 27 a andsecond journal part 27 b. Theeccentric parts eccentric parts airtight container 10 are made equal to each other. The eccentric part (hereinafter referred to as a first eccentric part) 28 a on one hand is accommodated in the first cylinder chamber. The eccentric part (hereinafter referred to as a second eccentric part) 28 b on the other hand is accommodated in the second cylinder chamber. -
Rollers eccentric part 28 a and secondeccentric part 28 b. Between the inner circumferential surface of each of therollers eccentric parts rollers eccentric parts shaft 15 rotates, each of therollers rollers - Inside each of the
first cylinder 13 andsecond cylinder 14, a vane (illustration omitted) is arranged. Each of the vanes is supported by each of thecylinders rollers cylinders rollers rollers - The high-temperature/high-pressure vapor-phase refrigerant compressed in each of the cylinder chambers of the
first cylinder 13 andsecond cylinder 14 is discharged into the inside of theairtight container 10 through each ofdischarge valve mechanisms airtight container 10. Furthermore, while the compression-mechanism unit 11 is in operation, the lubricating oil stored in theoil basin part 10 c of theairtight container 10 is stirred. The stirred lubricating oil is changed into a mist-like form and ascends inside theairtight container 10 toward thedischarge pipe 10 b under the favor of the flow of the vapor-phase refrigerant. Inside theairtight container 10, an oil separator or the like configured to separate the lubricating oil contained in the vapor-phase refrigerant ascending inside thecontainer 10 from the refrigerant is provided. - The electric-
motor unit 12 is accommodated in theairtight container 10 at an intermediate part along the central axis line O1 of theairtight container 10 in such a manner as to be positioned between the compression-mechanism unit 11 anddischarge pipe 10 b. The electric-motor unit 12 includes a so-called inner-rotor type motor and includes arotor 33 firmly fixed to therotating shaft 15 andstator 34 fixed to the inner circumferential surface of thecircumferential wall 10 a of theairtight container 10. A voltage is applied to the electric-motor unit 12 from the power source, whereby therotor 33 is rotated around the central axis line O1 relatively to thestator 34 androtating shaft 15 is rotated together with therotor 33. The rotatingshaft 15 is rotatably supported by the twobearings - One of the two
bearings first bearing 20 andsecond bearing 22 rotatably supports therotating shaft 15. Further, thefirst bearing 20 defines the top surface of the first cylinder chamber in thefirst cylinder 13 andsecond bearing 22 defines the undersurface of the second cylinder chamber in thesecond cylinder 14. The top surface is an end face of each of thecylinders rotating shaft 15, and undersurface is an end face of each of thecylinders first bearing 20 corresponds to a member blocking the first cylinder chamber from above, andsecond bearing 22 corresponds to a member blocking the second cylinder chamber from below. - The
first bearing 20 includes afirst flange part 20 a defining the top surface of the first cylinder chamber in thefirst cylinder 13 andfirst boss part 20 b upwardly extending in a cylindrical form so as to be continuous with thefirst flange part 20 a. - The
first flange part 20 a is positioned at the lower end of thefirst boss part 20 b, extends toward the outside of thefirst boss part 20 b in the radial direction thereof, and is continuous throughout the entire circumference of a circular shape concentric with the central axis of therotating shaft 15. In thefirst flange part 20 a, a discharge hole (hereinafter referred to as a first discharge hole) 20 c (seeFIG. 3 ) through which the refrigerant is discharged from the compression chamber of thefirst cylinder 13 is formed. The first discharge hole 20 c penetrates a part of thefirst flange part 20 a in the vertical direction and communicates with the inside of the compression chamber of thefirst cylinder 13. The first discharge hole 20 c is opened/closed by a predetermined valve mechanism (hereinafter referred to as a first discharge valve mechanism) 21. The firstdischarge valve mechanism 21 is arranged in thefirst flange part 20 a, opens the first discharge hole 20 c concomitantly with an increase in the pressure inside the compression chamber of thefirst cylinder 13 to thereby discharge the high-temperature/high-pressure vapor-phase refrigerant from the compression chamber. - The
first boss part 20 b is a part into which therotating shaft 15, more specifically, thefirst journal part 27 a is inserted at thefirst bearing 20, and which rotatably supports thefirst journal part 27 a. Thefirst boss part 20 b is arranged so as to be concentric with the rotatingshaft 15. That is, thefirst boss part 20 b is arranged perpendicular to thefirst flange part 20 a. In the state where thefirst journal part 27 a is inserted into thefirst boss part 20 b, the outer circumferential surface thereof is slid along the inner circumferential surface of thefirst boss part 20. - The
second bearing 22 includes asecond flange part 22 a defining the undersurface of the second cylinder chamber in thesecond cylinder 14 andsecond boss part 22 b downwardly extending in a cylindrical form so as to be continuous with thesecond flange part 22 a. - The
second flange part 22 a is positioned at the upper end of thesecond boss part 22 b, extends toward the outside of thesecond boss part 22 b in the radial direction thereof, and is continuous throughout the entire circumference of a circular shape concentric with the central axis of therotating shaft 15. In thesecond flange part 22 a, a discharge hole (illustration omitted, hereinafter referred to as a second discharge hole) through which the refrigerant is discharged from the compression chamber of thesecond cylinder 14 is formed. The second discharge hole penetrates a part of thesecond flange part 22 a in the vertical direction and communicates with the inside of the compression chamber of thesecond cylinder 14. The second discharge hole is opened/closed by a predetermined valve mechanism (hereinafter referred to as a second discharge valve mechanism) 23. The seconddischarge valve mechanism 23 opens the second discharge hole concomitantly with an increase in the pressure inside the compression chamber of thesecond cylinder 14 to thereby discharge the high-temperature/high-pressure vapor-phase refrigerant from the compression chamber. - The
second boss part 22 b is a part into which therotating shaft 15, more specifically, thesecond journal part 27 b is inserted at thesecond bearing 22, and which rotatably supports thesecond journal part 27 b. Thesecond boss part 22 b is arranged so as to be concentric with the rotatingshaft 15. That is, thesecond boss part 22 b is arranged perpendicular to thesecond flange part 22 a. In the state where thesecond journal part 27 b is inserted into thesecond boss part 22 b, the outer circumferential surface thereof is slid along the inner circumferential surface of thesecond boss part 22 b. - In each of
FIG. 3 andFIG. 4 , the configuration of the firstdischarge valve mechanism 21 is shown.FIG. 3 is a view schematically showing thefirst bearing 20 including the firstdischarge valve mechanism 21 from above.FIG. 4 is a cross-sectional view schematically showing thefirst bearing 20 at the part indicated by the arrows A3 shown inFIG. 3 . The configurations of the firstdischarge valve mechanism 21 and seconddischarge valve mechanism 23 are approximately equal to each other except for the fact that there is a point of difference incidental to the fact that themechanism 21 andmechanism 23 are positioned opposite to each other in the vertical direction. Accordingly, the configuration of the seconddischarge valve mechanism 23 conforms to the configuration shown inFIG. 3 andFIG. 4 . Accordingly, hereinafter the configuration example of the firstdischarge valve mechanism 21 will be described. - As shown in
FIG. 3 andFIG. 4 , the firstdischarge valve mechanism 21 is provided in thefirst flange part 20 a of thefirst bearing 20, appropriately opens the first discharge hole 20 c to thereby discharge the refrigerant compressed in the compression chamber of thefirst cylinder 13 from the compression chamber. The firstdischarge valve mechanism 21 includes adischarge valve 21 a andvalve presser 21 b. Thedischarge valve 21 a andvalve presser 21 b are fixed to thefirst flange part 20 a with a predetermined fixingmember 21 c. As the fixingmember 21 c, an arbitrary fixing member, for example, a bolt, screw, rivet or the like is applied. - The first discharge hole 20 c is opened at the bottom of a concave part (hereinafter referred to as a dug-down part) 20 d formed in the
first flange part 20 a. The dug-downpart 20 d is formed by making the top surface (end face on one end side in the axial direction of the rotating shaft 15) of thefirst flange part 20 a concave to a predetermined depth. The depth of the dug-downpart 20 d is made approximately equal to the dimension of the first discharge valve mechanism 21 (valve presser 21 b laid on top ofdischarge valve 21 a) in the vertical direction. The contour of the dug-downpart 20 d viewed from above thefirst flange part 20 a is made a similar figure of the contour slightly greater than the aforementioned contour of the firstdischarge valve mechanism 21 viewed from above thefirst flange part 20 a so that the first discharge valve mechanism 21 (discharge valve 21 a andvalve presser 21 b) can be installed inside the dug-downpart 20 d. That is, the longitudinal direction of the dug-downpart 20 d is parallel to the longitudinal direction of thedischarge valve 21 a andvalve presser 21 b to be described later. By making the dug-downpart 20 d have such a configuration, when the firstdischarge valve mechanism 21 is installed inside the dug-downpart 20 d, themechanism 21 is in a state where themechanism 21 is fully hidden in the dug-downpart 20 d. In other words, the dug-downpart 20 d is formed in thefirst flange part 20 a as a concave part in which the firstdischarge valve mechanism 21 is to be installed. It should be noted that in thesecond flange part 22 a of thesecond bearing 22, a dug-downpart 22d (seeFIG. 2 ) identical to the dug-downpart 20 d is formed as a concave part in which the seconddischarge valve mechanism 23 is to be installed. - The
discharge valve 21 a is a member configured to close or open the first discharge hole 20 c, and has a plate-like shape lengthwise in the predetermined direction. Thedischarge valve 21 a is formed of a material capable of elastic deformation such as spring steel or the like into an oblong card-like shape. Thereby, thedischarge valve 21 a is made to have a cantilever leaf spring structure capable of flexure deformation in the state where one end thereof in the longitudinal direction fixed by a fixingmember 21 c is made the fixed end, and the other end thereof in the longitudinal direction is made the free end. More specifically, when the high-temperature/high-pressure vapor-phase refrigerant compressed in the compression chamber of thefirst cylinder 13 reaches the predetermined discharge pressure, thedischarge valve 21 a undergoes deformation and opens the first discharge hole 20 c. Hereinafter, this state of thedischarge valve 21 a is referred to as the deformed state. In the state (hereinafter referred to as the normal state) before the first discharge hole 20 c is opened, thedischarge valve 21 a is in pressure contact with the circumferential edge of the first discharge hole 20 c in such a manner as to block up the first discharge hole 20 c by an elastic force (pressing force) less than the aforementioned predetermined discharge pressure. Accordingly, when the refrigerant exceeds the ambient pressure inside thefirst muffler 41 to reach the predetermined discharge pressure, the discharge pressure deforms thedischarge valve 21 a against the elastic force (pressing force) thereof to thereby make thedischarge valve 21 a open the first discharge hole 20 c and discharge the refrigerant. When the first discharge hole 20 c is opened to discharge the refrigerant and discharge pressure of the refrigerant becomes lower than the predetermined pressure, thedischarge valve 21 a is elastically restored from the deformed state to the normal state and blocks up the first discharge hole 20 c again. - The
valve presser 21 b is a member configured to restrain thedischarge valve 21 a from deformation, and has a plate-like shape lengthwise in the predetermined direction and having a thickness greater than thedischarge valve 21 a. Thevalve presser 21 b is formed of, for example, a steel material or the like. Thevalve presser 21 b is arranged in such a manner that the longitudinal direction thereof is made along the longitudinal direction of thedischarge valve 21 a. These longitudinal directions are directions intersecting the radial direction of thefirst flange part 20 a, in other words, the directions intersecting a plane including the central axis of therotating shaft 15. Further, these longitudinal directions are parallel to the longitudinal direction of the dug-downpart 20 d. In the example shown inFIG. 3 , the aforementioned longitudinal direction is the direction orthogonal to the radial direction of thefirst flange part 20 a, in other words, the direction orthogonal to the plane including the central axis of therotating shaft 15. Thevalve presser 21 b is arranged in such a manner as to be opposed to thedischarge valve 21 a in the process in which when opening the first discharge hole 20 c, thedischarge valve 21 a makes a displacement to a position separate from the first discharge hole 20 c. In the example shown inFIG. 3 andFIG. 4 , thevalve presser 21 b is arranged above thedischarge valve 21 a in such a manner as to cover thedischarge valve 21 a. Thevalve presser 21 b exhibits a bent (slightly levitated) state for opening the first discharge hole 20 c, i.e., a retroflex configuration conforming to the posture of thedischarge valve 21 a in the deformed state. Thereby, when thedischarge valve 21 a undergoes flexure deformation so as to open the first discharge hole 20 c, i.e., when thedischarge valve 21 a enters the deformed state, thevalve presser 21 b gets contact with thedeformed discharge valve 21 a to thereby prevent thedischarge valve 21 a from undergoing further deformation (levitation). - On the
first bearing 20, a muffler (hereinafter referred to as a first muffler) 41 configured to cover thefirst bearing 20 is provided. Thefirst muffler 41 suppresses pulsation and noise caused by, for example, the refrigerant to be discharged from the compression chamber of thefirst cylinder 13 into the inside of theairtight container 10. Thefirst muffler 41 covers thefirst bearing 20 so as to surround the part between thefirst flange part 20 a andfirst boss part 20 b, and forms afirst muffler chamber 43 between thefirst flange part 20 a andfirst boss part 20 b. Thefirst muffler chamber 43 is a space into which the high-temperature/high-pressure refrigerant compressed in the compression chamber of thefirst cylinder 13 is discharge from the first discharge hole 20 c in the first place. Thefirst muffler 41 includes communicatingholes 41 a configured to make the inside and outside (space above and below the first muffler wall) of thefirst muffler 41 communicate with each other. The high-temperature/high-pressure vapor-phase refrigerant discharged into thefirst muffler chamber 43 through the first discharge hole 20 c is discharged into the inside of theairtight container 10 through the communicatingholes 41 a. - As shown in
FIG. 2 , under thesecond bearing 22, a muffler (hereinafter referred to as a second muffler) 42 configured to cover thesecond bearing 22 is provided. Thesecond muffler 42 suppresses pulsation and noise caused by, for example, the refrigerant to be discharged from the compression chamber of thesecond cylinder 14 into the inside of theairtight container 10. Thesecond muffler 42 covers thesecond bearing 22 so as to surround the part between thesecond flange part 22 a andsecond boss part 22 b, and forms asecond muffler chamber 44 between thesecond flange part 22 a andsecond boss part 22 b. Thesecond muffler chamber 44 is a space into which the high-temperature/high-pressure refrigerant compressed in the compression chamber of thesecond cylinder 14 is discharge from the second discharge hole in the first place. Thesecond muffler chamber 44 communicates with thefirst muffler chamber 43 through a communicating hole provided in the compression-mechanism unit 11. The communicating hole penetrates each of thesecond flange part 22 a,second cylinder 14,partition plate 18,first cylinder 13, andfirst flange part 20 a and is opened to thesecond muffler chamber 44 andfirst muffler chamber 43. The high-temperature/high-pressure vapor-phase refrigerant discharged into thesecond muffler chamber 44 through the second discharge hole reaches thefirst muffler chamber 43 through the aforementioned communicating hole and is thereafter discharged into the inside of theairtight container 10 through the communicatingholes 41 a. - In
FIG. 5 andFIG. 6 , the configuration of thefirst muffler 41 according to this embodiment is shown.FIG. 5 is a view schematically showing, from above, the state where thefirst muffler 41 is mounted on thefirst bearing 20.FIG. 6 is a perspective view schematically showing thefirst muffler 41. - As shown in
FIGS. 4 to 6 , thefirst muffler 41 is a three-dimensional component including anend face part 45, side facepart 46, and brimpart 47, and these three parts are formed so as to have a thin-walled structure. The end facepart 45, side facepart 46, and brimpart 47 define the outer contour of thefirst muffler chamber 43. The end facepart 45 is a face part of thefirst muffler 41 on one end side thereof in the axial direction (direction along the central axis line O1 of the airtight container 10) of therotating shaft 15 and is a face part radially spreading relatively to the central axis of therotating shaft 15. In the example shown inFIG. 5 andFIG. 6 , the end facepart 45 corresponds to the top face part of thefirst muffler 41. The end facepart 45 has an annular shape including acircular opening 45 a in which thefirst boss part 20 b of thefirst bearing 20 is to be inserted. The center of the opening 45 a is positioned on the central axis (central axis line O1 of the airtight container 10) of therotating shaft 15. In other words, thefirst muffler 41 is arranged in such a manner that the opening 45 a is concentric with the rotatingshaft 15. The bore diameter (distance across the opening) of the opening 45 a is made approximately equal to the dimension of the outer diameter of thefirst boss part 20 b at the insertion portion. - The end face
part 45 includes fivepiece parts 45 b to 45 f radially extending relatively to the center of the opening 45 a. The fivepiece parts 45 b to 45 f are arranged at approximately regular intervals in the circumferential direction of the opening 45 a. The fivepiece parts 45 b to 45 f are, except for the part between thepiece part 45 b and piecepart 45 f, gently continuous with each other in such a manner that adjacent piece parts gradually become closer to the centerline (central axis line O1 of the airtight container 10) of the opening 45 a. Of the five piece parts, each of the fourpiece parts 45 c to 45 f includes a communicatinghole 41 a formed therein. It should be noted that the number of the piece parts included in the end face part is not limited to five, and may less than or equal to four, or may be greater than or equal to six. - The side face
part 46 joins the end face part 45 (specifically, fivepiece parts 45 b to 45 f) and brimpart 47 to each other in a cylindrical form throughout the entire circumference in the circumferential direction of the opening 45 a, in other words, the central axis of therotating shaft 15. - That is, the side face
part 46 corresponds to the outer circumferential part of thefirst muffler 41. Regarding the side facepart 46, the part on the upper side thereof continuous with the end facepart 45 has a cylindrical shape thinner than the part on the lower side thereof continuous with thebrim part 47. In other words, the side facepart 46 is inclined in such a manner that the greater the distance from one side thereof continuous with thebrim part 47 toward the other side thereof continuous with the end facepart 45, the closer to the centerline (central axis line O1 of the airtight container 10) of the opening 45 a the side facepart 46 becomes. - The
brim part 47 is a face part of thefirst muffler 41 on the other end side thereof in the axial direction (direction along the central axis line O1 of the airtight container 10) of therotating shaft 15, and is a face part spreading approximately in parallel with the end facepart 45 in a circular form concentric with the central axis of therotating shaft 15. In the example shown inFIG. 5 andFIG. 6 , thebrim part 47 corresponds to the undersurface part of thefirst muffler 41, and is continuous with the side facepart 46 at a part of thefirst muffler 41 on the lower end side thereof. Thebrim part 47 includes through-holes into which the bolts are to be inserted. The bolt is an example of a fixing member (in this embodiment, a second fixing member used to fix the first muffler 41) configured to fix thefirst muffler 41 to thefirst flange part 20 a. In the example shown inFIG. 5 andFIG. 6 , thebrim part 47 includes five through-holes 47 a to 47 e. Into each of these through-holes 47 a to 47 e, one bolt is inserted and, in total fivebolts 48 a to 48 e are inserted into these through-holes 47 a to 47 e. These through-holes 47 a to 47 e are arranged alongside at approximately regular intervals in the circumferential direction of the opening 45 a. When viewed from the axial direction of therotating shaft 15, the five through-holes 47 a to 47 e are arranged in such a manner that the each of the through-holes 47 a to 47 e is positioned betweenpiece parts 45 b to 45 f adjacent to each other at the end facepart 45. In other words, the five through-holes 47 a to 47 e and fivepiece parts 45 b to 45 f are arranged in such a manner that the through-holes 47 a to 47 e andpiece parts 45 b to 45 f are alternately positioned in the circumferential direction of the opening 45 a with approximately equal phase angle differences held between the alternately arranged through-holes 47 a to 47 e andpiece parts 45 b to 45 f. It should be noted that the number of the through-holes possessed by the brim part is not limited to five, and may be less than or equal to four, or greater than or equal to six. For example, it is sufficient if the number of the through-holes included in the brim part is made equal to the number of the piece parts included in the end face part. - The through-
holes 47 a to 47 e respectively communicate with the through-holes 20 f to 20 j formed in thefirst flange part 20 a of thefirst bearing 20. In the example shown inFIGS. 3 to 6 , the first through-hole 47 a communicates with the first through-hole 20 f. Into these through-holes bolt 48 a is inserted. Likewise, the second through-hole 47 b communicates with the second through-hole 20 g. Into these through-holes bolt 48 b is inserted. The third through-hole 47 c communicates with the third through-hole 20 h. Into these through-holes bolt 48 c is inserted. The fourth through-hole 47 d communicates with the fourth through-hole 20 i. Into these through-holes 47 d and 20 i communicating with each other, thebolt 48 d is inserted. The fifth through-hole 47 e communicates with the fifth through-hole 20 j. Into these through-holes bolt 48 e is inserted. Thesebolts 48 a to 48 e are each fastened to thefirst cylinder 13. Thereby, thefirst muffler 41 andfirst bearing 20 are implemented on thefirst cylinder 13. In other words, thebrim part 47 is fixed to thefirst cylinder 13 through thefirst flange part 20 a of thefirst bearing 20 with thebolts 48 a to 48 e. That is, thebolts 48 a to 48 e fix thebrim part 47 to thefirst cylinder 13 through thefirst flange part 20 a. - The
first muffler 41 includes aconcave part 49 formed by inwardly denting a part of the portion defining the outer contour of thefirst muffler chamber 43 to be formed by thefirst muffler 41 toward the inside of thefirst muffler chamber 43. Hereinafter, the configuration of theconcave part 49 will be described with reference toFIGS. 4 to 6 . - The
concave part 49 has a configuration formed by denting each of the end facepart 45 and side facepart 46 toward the inside of thefirst muffler chamber 43. When viewed from thefirst muffler chamber 43, theconcave part 49 is a convex part protruding into thefirst muffler chamber 43 and corresponds to a rib of thefirst muffler 41. That is, theconcave part 49 functions as a reinforcing part configured to suppress deformation of thefirst muffler 41. In the example shown inFIGS. 4 to 6 , theconcave part 49 has the configuration formed by denting each of the portion between thepiece part 45 b and piecepart 45 f at the end facepart 45 and portion connecting between thepiece part 45 b,piece part 45 f, and brimpart 47 at the side facepart 46 toward the inside of thefirst muffler chamber 43. - When projected onto the
top surface 20 e of thefirst flange part 20 a from the axial direction of therotating shaft 15, theconcave part 49 is arranged in such a manner as to intersect the longitudinal direction of the dug-downpart 20 d and thereby overlap the dug-downpart 20 d. That is, theconcave part 49 is arranged in the vicinity of the dug-downpart 20 d, in other words, in the vicinity of thedischarge valve 21 a andvalve presser 21 b. - The
concave part 49 is configured to include fourface parts 49 a to 49 d as the main face parts. Thefirst face part 49 a andsecond face part 49 b are opposed to each other as a pair approximately in parallel with each other in the circumferential direction of the opening 45 a. Further, thefirst face part 49 a andsecond face part 49 b are parallel to a predetermined plane (virtual plane) including the central axis of therotating shaft 15 and intersecting the longitudinal direction of thedischarge valve 21 a. - In this embodiment, as one example, the
first face part 49 a andsecond face part 49 b are parallel to the plane including the central axis of therotating shaft 15 and orthogonal to the longitudinal direction of thedischarge valve 21 a. From another point of view, when theconcave part 49 is projected onto thetop surface 20 e of thefirst flange part 20 a from the axial direction of therotating shaft 15, thefirst face part 49 a andsecond face part 49 b are arranged in such a manner as to intersect the longitudinal direction of the dug-downpart 20 d, i.e., in this case, as to intersect the longitudinal direction of the dug-downpart 20 d at right angles and thereby overlap the dug-downpart 20 d, i.e., thedischarge valve 21 a andvalve presser 21 b. - The
third face part 49 c andfourth face part 49 d are face parts continuous with each other and connecting between thefirst face part 49 a andsecond face part 49 b. Thefirst face part 49 a andsecond face part 49 b are continuous with each other through thethird face part 49 c andfourth face part 49 d. Thethird face part 49 c rises approximately in parallel with the centerline (central axis line O1 of the airtight container 10) of the opening 45 a, and connects between thefirst face part 49 a andsecond face part 49 b at the upper part thereof. Thefourth face part 49 d rises so as to be inclined toward the centerline (central axis line O1 of the airtight container 10) of the opening 45 a, and connects between thefirst face part 49 a andsecond face part 49 b at the lower part thereof. Thefourth face part 49 d is inclined in such a manner that the closer to one side (in this case, upper side) thereof continuous with thethird face part 49 c, the closer to the centerline (central axis line O1 of the airtight container 10) of the opening 45 a becomes thefourth face part 49 d. Thethird face part 49 c andfourth face part 49 d are perpendicularly continuous with thefirst face part 49 a andsecond face part 49 b. - The
third face part 49 c includes a through-hole 49 e into which abolt 50 is to be inserted. Thebolt 50 is an example of a fixing member (in this embodiment, a first fixing member configured to fix the first muffler 41) configured to fix thefirst muffler 41, specifically, the side facepart 46 to thefirst boss part 20 b. As shown inFIG. 5 , on thefirst boss part 20 b, a seating face part 20 k including a flat seating face capable of coming into contact with thethird face part 49 c is provided. Thebolt 50 is fastened to a bolt-hole 201 formed in the seating face part 20 k. Further, thefirst face part 49 a andsecond face part 49 b are in opposition to each other with a separation distance (clearance) for prevention of interference with thehead 50 a of thebolt 50 held between theface parts - As described above, the
first muffler 41 is fixed to thefirst cylinder 13 is fixed to thefirst bearing 20, i.e., to thefirst cylinder 13 through thefirst flange part 20 a with thebolts 48 a to 48 e, and is fixed to thefirst boss part 20 b with thebolt 50. Thefirst flange part 20 a is arranged in such a manner as to outwardly extend in the radial direction of therotating shaft 15, andfirst boss part 20 b is arranged concentric with the rotatingshaft 15. That is, thefirst flange part 20 a andfirst boss part 20 b are arranged orthogonal to each other. Accordingly, it is possible to firmly fix thefirst muffler 41 to thefirst bearing 20 in two directions, i.e., in the radial direction and axial direction of therotating shaft 15. Thereby, it is possible to enhance the stiffness of thefirst muffler 41 against, for example, the inclination of thefirst boss part 20 b at the time of rotation of therotating shaft 15. - Further, the
first muffler 41 includes theconcave part 49 arranged in the vicinity of the dug-downpart 20 d of thefirst flange part 20 a. As described above, theconcave part 49 functions as a reinforcing part configured to suppress deformation of thefirst muffler 41. Accordingly, it is possible for theconcave part 49, when the rotatingshaft 15 is rotated, to bear the burden of the force attempting to make the dug-downpart 20 d undergo elastic deformation so as to incline thefirst boss part 20 b toward, for example, thefirst flange part 20 a. Owing to this, it is possible to suppress the elastic deformation of the dug-downpart 20 d, and suppress such a deformation as to incline thefirst boss part 20 b toward thefirst flange part 20 a. As a result, it becomes possible to reduce the noise caused by, for example, the bending vibration of therotating shaft 15. - It should be noted that the
second muffler 42 includes no part corresponding to theconcave part 49 possessed by the aforementionedfirst muffler 41. This is due to the following reason. As shown inFIG. 2 , regarding thesecond boss part 22 b of thesecond bearing 22, the length of therotating shaft 15 in the axial direction thereof is less than thefirst boss part 20 b of thefirst bearing 20. That is, such a deformation as to incline thesecond boss part 22 b toward thesecond flange part 22 a hardly occurs to thesecond boss part 22 b and, even when deformed, thesecond boss part 22 b is not so largely deformed as thefirst boss part 20 b. Accordingly, in this embodiment, thesecond muffler 42 has the configuration in which the part corresponding to theconcave part 49 is omitted. That is, thesecond muffler 42 can be configured in the same manner as thefirst muffler 41 except for the differences incidental to the point that thesecond muffler 42 has no part corresponding to theconcave part 49 and point that thesecond muffler 42 is positioned opposite (upside down) in the vertical direction to thefirst muffler 41. However, thesecond muffler 42 may have a concave part identical to thefirst muffler 41. - While certain embodiments have been described, these embodiments have been presented by way of example only, and are not intended to limit the scope of the inventions. Indeed, the novel embodiments described herein may be embodied in a variety of other forms; furthermore, various omissions, substitutions and changes in the form of the embodiments described herein may be made without departing from the spirit of the inventions. The accompanying claims and their equivalents are intended to cover such forms or modifications as would fall within the scope and spirit of the inventions.
Claims (6)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2021-140934 | 2021-08-31 | ||
JP2021140934A JP2023034612A (en) | 2021-08-31 | 2021-08-31 | Compressor, and air conditioner |
Publications (1)
Publication Number | Publication Date |
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US20230064536A1 true US20230064536A1 (en) | 2023-03-02 |
Family
ID=85286763
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US17/654,437 Abandoned US20230064536A1 (en) | 2021-08-31 | 2022-03-11 | Compressor and air conditioner |
Country Status (3)
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US (1) | US20230064536A1 (en) |
JP (1) | JP2023034612A (en) |
CN (1) | CN115726966A (en) |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9004888B2 (en) * | 2012-10-30 | 2015-04-14 | Fujitsu General Limited | Rotary compressor having discharge groove to communicate compression chamber with discharge port near vane groove |
US9017048B2 (en) * | 2008-08-22 | 2015-04-28 | Lg Electronics Inc. | Variable capacity type rotary compressor, cooling apparatus having the same, and method for driving the same |
-
2021
- 2021-08-31 JP JP2021140934A patent/JP2023034612A/en active Pending
-
2022
- 2022-03-10 CN CN202210230499.XA patent/CN115726966A/en active Pending
- 2022-03-11 US US17/654,437 patent/US20230064536A1/en not_active Abandoned
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9017048B2 (en) * | 2008-08-22 | 2015-04-28 | Lg Electronics Inc. | Variable capacity type rotary compressor, cooling apparatus having the same, and method for driving the same |
US9004888B2 (en) * | 2012-10-30 | 2015-04-14 | Fujitsu General Limited | Rotary compressor having discharge groove to communicate compression chamber with discharge port near vane groove |
Also Published As
Publication number | Publication date |
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CN115726966A (en) | 2023-03-03 |
JP2023034612A (en) | 2023-03-13 |
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