EP3434902A1 - Hermetic rotary compressor and refrigeration cycle device - Google Patents
Hermetic rotary compressor and refrigeration cycle device Download PDFInfo
- Publication number
- EP3434902A1 EP3434902A1 EP17770180.2A EP17770180A EP3434902A1 EP 3434902 A1 EP3434902 A1 EP 3434902A1 EP 17770180 A EP17770180 A EP 17770180A EP 3434902 A1 EP3434902 A1 EP 3434902A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cylinder
- case
- hermetic
- compression mechanism
- rotating shaft
- 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.)
- Granted
Links
- 238000005057 refrigeration Methods 0.000 title claims abstract description 18
- 230000006835 compression Effects 0.000 claims abstract description 63
- 238000007906 compression Methods 0.000 claims abstract description 63
- 239000003507 refrigerant Substances 0.000 claims description 25
- 239000012530 fluid Substances 0.000 claims description 17
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 claims description 13
- 239000006096 absorbing agent Substances 0.000 claims description 9
- 229910002092 carbon dioxide Inorganic materials 0.000 claims description 7
- 239000001569 carbon dioxide Substances 0.000 claims description 7
- 230000000149 penetrating effect Effects 0.000 claims description 3
- 230000001965 increasing effect Effects 0.000 abstract description 5
- 239000010687 lubricating oil Substances 0.000 description 7
- 238000005192 partition Methods 0.000 description 7
- 239000003921 oil Substances 0.000 description 5
- 230000000717 retained effect Effects 0.000 description 3
- 238000003466 welding Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000000452 restraining effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 239000013585 weight reducing agent Substances 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
- 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
-
- 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
- F04C23/003—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 having complementary function
-
- 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
Definitions
- Embodiments described herein relate generally to a hermetic rotary compressor and refrigeration cycle device provided with the hermetic rotary compressor.
- a hermetic rotary compressor is provided with a hermetic case configured to accommodate therein an electric motor section and compression mechanism section.
- the hermetic case is constituted of, for example, a cylindrical main case and lid-like end cases, and the end cases having an identical diameter are fitted into both ends of the main case to thereby hermetically seal the hermetic case.
- FIG. 1 of Patent Literature 1 a rotary compressor in which a hermetic case is hermetically sealed by inserting end cases having diameters smaller than an inner diameter of a main case into both ends of the main case is disclosed.
- a cylinder disclosed in Patent Literature 1 is formed smaller than an inner diameter of the end case.
- a carbon dioxide refrigerant has been brought into use as a working fluid of a refrigeration cycle device.
- a carbon dioxide refrigerant has working pressure higher than a hitherto used HFC-based refrigerant, and hence it is necessary to enhance the pressure resistance of the hermetic case.
- the end case is made larger in the axial direction, thereby upsizing the hermetic rotary compressor.
- Patent Literature 1 JP 3958443 B
- Embodiments described herein aim to provide a hermetic rotary compressor capable of improving the pressure resistance of the hermetic case and restraining upsizing of the hermetic case, and refrigeration cycle device provided with the hermetic rotary compressor.
- a hermetic rotary compressor comprises a hermetic case, a rotating shaft, an electric motor section and a plurality of compression mechanism sections.
- the rotating shaft, the electric motor section and the compression mechanism sections are accommodated in the hermetic case.
- the electric motor section rotates the rotating shaft.
- the compression mechanism sections are coupled to the rotating shaft, and compress a working fluid.
- the compression mechanism sections include a first compression mechanism section and a second compression mechanism section.
- the first compression mechanism section is provided with a first cylinder
- the second compression mechanism section is provided with a second cylinder.
- the hermetic case is provided with a main case and end cases.
- the main case includes openings and the end cases are fitted into the openings.
- the whole of the first cylinder is positioned inside the main case in an axial direction of the rotating shaft, and at least part of the second cylinder is positioned inside the end case.
- the maximum distance from a center of the rotating shaft to an outer circumference of the first cylinder is greater than the maximum distance from the center of the rotating shaft to an inner circumference of the end case.
- a refrigeration cycle device of an embodiment is provided with the aforementioned hermetic rotary compressor and a refrigeration cycle circuit.
- a heat radiator, expanding device, and heat absorber are connected to each other in sequence, and a working fluid circulates through the circuit.
- the hermetic rotary compressor is connected to the refrigeration cycle circuit between the heat radiator and heat absorber.
- FIG. 1 is a cross-sectional view showing an example of a hermetic rotary compressor K of a first embodiment. Further, FIG. 1 also shows the configuration of a refrigeration cycle device provided with the hermetic rotary compressor K at the same time.
- the hermetic rotary compressor K will be simply referred to as a compressor K.
- the refrigeration cycle device includes, as major elements, a compressor K, heat radiator 2, expanding device 3, and heat absorber 4.
- the heat radiator 2, expanding device 3, and heat absorber 4 are connected to each other in sequence through refrigerant pipes P.
- the compressor K is connected between the heat radiator 2 and heat absorber 4.
- An accumulator 5 is annexed to the compressor K.
- the major elements of the refrigeration cycle device constitute a refrigeration cycle circuit T through which the working fluid circulates.
- the compressor K is provided with a hermetic case 10, electric motor section 11, and compression element 12 constituted of a plurality of compression mechanism sections, and rotating shaft 13.
- the electric motor section 11 is an example of a driving element.
- the electric motor section 11 and compression element 12 are accommodated in the hermetic case 10 and are coupled to each other through the rotating shaft 13.
- the compressor K is configured as a vertical rotary compressor. It should be noted that the compressor K is not limited to the vertical type, and may also be a horizontal rotary compressor.
- a direction from the electric motor section 11 toward the compression element 12 along the rotating shaft 13 is called a "downward direction” or a “lower part” and, a direction opposite thereto is called an "upward direction” or an “upper part”.
- a length in the axial direction of the rotating shaft 13 is simply referred to as a "height".
- the compressor K of the first embodiment uses a carbon dioxide (CO 2 ) refrigerant as the working fluid.
- the carbon dioxide refrigerant has working pressure higher than the HFC-based refrigerant. Accordingly, high pressure resistance is required of the hermetic case 10 of the compressor K.
- the hermetic case 10 is constituted of a main case 10a, lower end case 10c, and upper end case 10b.
- the main case 10a is formed into a cylindrical shape both ends of which are opened.
- the lower end case 10c is formed into a dish-like shape having an outer diameter smaller than an inner diameter of the main case 10a, and is fitted into a lower end of the main case 10a.
- the lower end case 10c is an example of an end case.
- the upper end case 10b has a shape roughly identical to the lower end case 10c, and is fitted into an upper end of the main case 10a.
- the lower end case 10c and upper end case 10b are coupled to the main case by welding or the like.
- the main case 10a and upper end case 10b may be formed integral with each other to thereby form a closed-end cylindrical configuration.
- the upper end case 10b is another example of an end case.
- a carbon dioxide refrigerant having high working pressure is used, and hence the main case 10a, upper end case 10b, and lower end case 10c constituting the hermetic case 10 each have a heavy wall thickness.
- a wall thickness of a hermetic case using an HFC-based refrigerant is, for example, 3 to 4 mm.
- a wall thickness of the hermetic case 10 according to the first embodiment is, for example, 7 to 8 mm.
- each of the end cases of the hermetic case 10 is not formed into a flat-plate shape, and is formed into a dish-like shape, and hence the pressure resistance thereof can be enhanced.
- the end cases are fitted into the main case 10a, and hence the end cases can be made compact in size.
- An outer diameter of the end case is smaller than an outer diameter of the main case 10a by twice the wall thickness.
- a suction refrigerant pipe Pa and lead-out refrigerant pipe Pb are attached to the hermetic case 10.
- the suction refrigerant pipe Pa penetrates the main case 10a to thereby make the inside and outside of the hermetic case 10 communicate with each other.
- the lead-out refrigerant pipe Pb penetrates the upper end case 10b to thereby make the inside and outside of the hermetic case 10 communicate with each other.
- the suction refrigerant pipe Pa is connected to the heat absorber 4 through the accumulator 5.
- the lead-out refrigerant pipe Pb is connected to the heat radiator 2.
- the electric motor section 11 is provided with a stator 15 and rotor 16.
- the rotor 16 is fixed to the rotating shaft 13.
- the stator 15 is fixed to an inner circumferential surface of the hermetic case 10.
- An inner circumferential surface of the stator 15 is opposed to an outer circumferential surface of the rotor 16 with a slight gap held between them.
- the compression element 12 is positioned beneath the electric motor section 11 serving as a driving element.
- the compression element 12 is provided with, for example, a first compression mechanism section 18A, second compression mechanism section 18B, intermediate partition plate 20, main bearing 23, sub-bearing 24, and valve covers 27 and 28.
- the first and second compression mechanism sections 18A and 18B are provided with first and second cylinders 21 and 22, respectively.
- the compression element 12 is an example of a plurality of compression mechanism sections. It should be noted that the number of compression mechanism sections is not limited to two cylinders.
- the compression element 12 may be of a multi-cylinder type including third and fourth compression mechanism sections in addition to the first and second compression mechanism sections 18A and 18B.
- the main bearing 23 is fixed to the inner circumferential surface of the hermetic case 10 by, for example, welding.
- the valve cover 27, main bearing 23, first cylinder 21, intermediate partition plate 20, second cylinder 22, sub-bearing 24, and valve cover 28 are laid one on top of another in sequence from the electric motor section 11 side, and are fixed to each other by, for example, jointly fastening.
- the main bearing 23 and sub-bearing 24 rotatably support the rotating shaft 13.
- the valve covers 27 and 28 cover the main bearing 23 and sub-bearing 24, respectively.
- An undersurface of the sub-bearing 24 is an example of an end section of the compression element 12.
- first cylinder 21 a circular first cylinder chamber Sa interposed between the main bearing 23 and intermediate partition plate 20 is formed.
- second cylinder 22 a circular second cylinder chamber Sb interposed between the intermediate partition plate 20 and sub-bearing 24 is formed.
- Each of the first and second cylinder chambers Sa and Sb is formed into a shape having an identical diameter and height.
- the rotating shaft 13 includes first and second eccentric sections a and b protruding in directions perpendicular to the axial direction.
- the first and second eccentric sections a and b are arranged in such a manner as to be shifted from each other by, for example, 180° with respect to the center of the rotating shaft 13.
- Cylindrical rollers 25 and 26 are respectively fitted on the first and second eccentric sections a and b.
- the first eccentric section a and roller 25 are arranged in the first cylinder chamber Sa.
- the second eccentric section b and roller 26 are arranged in the second cylinder chamber Sb.
- a blade storing groove extending in a radial direction of the first cylinder chamber Sa is formed in the first cylinder 21 .
- a blade storing groove extending in a radial direction of the second cylinder chamber Sb is formed in the second cylinder 22 .
- blades 30 and 32 are respectively stored in a protrudable/retractable manner.
- a tip end of the blade 30 is in slidable contact with an outer circumferential surface of the roller 25 to thereby separate the first cylinder chamber Sa into two parts.
- a tip end of the blade 32 is in slidable contact with an outer circumferential surface of the roller 26 to thereby separate the second cylinder chamber Sb into two parts.
- a horizontal hole configured to arrange therein a coil spring 31 is formed.
- a base end of the blade 30 is pressed against the roller 25 by the coil spring 31.
- the coil spring 31 is an example of an elastically energizing member.
- the blade storing groove of the second cylinder 22 no horizontal hole for arranging therein a coil spring 31 is formed.
- the blade storing groove of the second cylinder 22 communicates with the inside of the hermetic case 10.
- a base end of the blade 32 is pressed against the roller 26 by the pressure of the working fluid filling the hermetic case 10.
- the blade 30 of the first compression mechanism section 18A is provided with the elastically energizing member, and hence is pressed against the roller 25 at all times without being subject to the pressure inside the hermetic case 10.
- the blade 32 of the second compression mechanism section 18B is not pressed against the roller 26 immediately after starting of the electric motor section 11 when the pressure inside the hermetic case 10 is low.
- the blade 32 enters a state where the blade 32 is pressed against the roller 26.
- the second cylinder 22 has no need of space for arrangement of the elastically energizing member, and hence can be configured more compact in size than the first cylinder 21.
- a horizontal hole for arrangement of the elastically energizing member is not formed, and hence, although the second cylinder 22 is smaller than the first cylinder 21 in diameter, sufficient pressure resistance can be secured.
- a suction hole is formed in the first cylinder 21, a suction hole is formed.
- the aforementioned suction refrigerant pipe Pa is inserted.
- the suction hole and inside of the second cylinder chamber Sb communicate with each other by a branch suction path.
- the suction hole and branch suction path will be described later with reference to FIG. 2 .
- the working fluid to be supplied from the refrigeration cycle circuit T through the suction refrigerant pipe Pa is guided from the suction hole to the first cylinder chamber Sa, and is then guided from the branch suction path to the second cylinder chamber Sb.
- the working fluid is compressed by the first and second cylinder chambers Sa and Sb concomitantly with the rotation of the rotating shaft 13.
- the working fluid compressed by the first cylinder chamber Sa is discharged into the inside of valve cover 27 through a discharge valve mechanism provided to the main bearing 23, and is then supplied to the inside of the hermetic case 10 from a discharge hole formed in the valve cover 27.
- the working fluid compressed by the second cylinder chamber Sb is discharged into the inside of the valve cover 28 through a discharge valve mechanism provided to the sub-bearing 24.
- the inside of the valve cover 28 communicates with the inside of the valve cover 27 by a discharge gas guide passage penetrating the main bearing 23, first cylinder 21, intermediate partition plate 20, second cylinder 22, and sub-bearing 24.
- the working fluid discharged into the inside of the valve cover 28 is supplied to the inside of the hermetic case 10 through the inside of the valve cover 27.
- the whole of the first cylinder 21 is positioned inside the main case 10a.
- At least part of the second cylinder 22 is positioned inside the lower end case 10c.
- the compressor K of the first embodiment is characterized in that the maximum distance L from the center of the rotating shaft 13 to the outer circumference of the first cylinder 21 is greater than the maximum distance M from the center of the rotating shaft 13 to the inner circumference of the lower end case 10c. Accordingly, the maximum distance L from the center of the rotating shaft 13 to the outer circumference of the first cylinder 21 is greater than the maximum distance from the center of the rotating shaft 13 to the outer circumference of the second cylinder 22.
- the second cylinder 22 is formed more compact than the first cylinder 21 in size.
- the compressor K of the first embodiment configured as described above is provided with the compression element 12 constituted of a plurality of compression mechanism sections.
- the second compression mechanism section 18B is configured in such a manner that at least part of the second cylinder 22 thereof is positioned inside the lower end case 10c in the axial direction of the rotating shaft 13.
- the dimension of the lower end case 10c becomes larger in the axial direction of the rotating shaft 13.
- at least part of the second cylinder 22 is positioned inside the lower end case 10c in the axial direction of the rotating shaft 13.
- the second cylinder 22 it is possible to allow at least part of the second cylinder 22 to be positioned inside the lower end case 10c, and thereby form the main case 10a short, and hence it is possible to prevent the hermetic case 10 from becoming larger in size while enhancing the pressure resistance.
- the lower end case 10c according to the first embodiment is fitted into the main case 10a, and the lower end case 10c can be formed smaller in diameter than the main case 10a in the radial direction. In the first embodiment, even when the lower end case 10c is made larger in the axial direction, the oil basin section Z formed by the lower end case 10c does not become excessively large in the radial direction.
- the second compression mechanism section 18B according to the first embodiment utilizes the pressure inside the hermetic case 10 as means for pressing the blade 32. It is not necessary to form a horizontal hole configured to provide therein a coil spring 31 in the second cylinder 22 according to the first embodiment.
- the horizontal hole making the rigidity the lowest in the cylinder is made unnecessary, and hence, even when the maximum distance from the center of the rotating shaft 13 to the outer circumference of the second cylinder 22 is made small, the rigidity of the second cylinder 22 can be secured.
- the second cylinder 22 can be formed small, and hence as described previously it is possible to configure a compressor K in which at least part of the second cylinder 22 is made inside the lower end case 10c.
- the first compression mechanism section 18A is configured in such a manner that the whole of the first cylinder 21 is positioned inside the main case 10a in the axial direction of the rotating shaft 13, and thus the outer diameter of the first cylinder 21 can be made larger than the inner circumference of the lower end case 10c.
- At least one cylinder should be provided with a blade 30 pressed by an elastically energizing member.
- the horizontal hole storing therein the elastically energizing member is the part at which the rigidity is the lowest in the cylinder.
- At least one cylinder is connected to the suction refrigerant pipe Pa penetrating the cylinder.
- the suction hole (d) in which the suction refrigerant pipe Pa is to be inserted is the part at which the rigidity is the lowest in the cylinder as in the case of the horizontal hole configured to store therein the elastically energizing member.
- the horizontal hole and suction hole (d) are formed in only the first cylinder 21 having a sufficient wall thickness, and these holes are not formed in another cylinder. According to the first embodiment, it is possible to form the first cylinder 21 larger in the radial direction, and secure a sufficient wall thickness. Accordingly, even when the horizontal hole and suction hole (d) are formed in the first cylinder 21, rigidity can be secured to the first cylinder 21.
- FIG. 2 is a cross-sectional view showing an example of a hermetic rotary compressor Ka of a second embodiment.
- the configuration of a main bearing 23 differs from the main bearing 23 of the first embodiment.
- Other configurations are identical to the first embodiment. Configurations having functions identical to or similar to the configurations described in the first embodiment are denoted by reference symbols identical to the first embodiment to thereby enable reference to corresponding descriptions of the first embodiment, and duplicated descriptions are omitted.
- a main bearing 23 is divided into frames 230a and 230b.
- the frame 230a is fixed to an inner circumferential surface of a hermetic case 10 by, for example, welding.
- the frame 230b is fixed to the frame 230a by means of a fixing bolt 35, and rotatably supports a rotating shaft 13.
- the frame 230a is fixed to the inner circumferential surface of the main case 10a as a single item. Subsequently, the frame 230b in a state where first and second cylinders 21 and 22 are attached thereto is fixed to the frame 230a.
- the main bearing 23 is divided into the frames 230a and 230b, whereby it is possible to further enhance the assembly accuracy of the frame 230a with respect to the main case 10a.
- the first cylinder 21 is formed in such a manner that the maximum distance L from the center of the rotation shaft 13 to the outer circumference of the first cylinder 21 is made larger than the maximum distance M from the center of the rotating shaft 13 to the inner circumference of the lower end case 10c.
- the first cylinder 21 is sufficiently large in size, and hence even when a screw hole for fastening by the fixing bolt 35 is formed therein, the rigidity of the first cylinder 21 can be secured.
- the second cylinder 22 is formed smaller than the first cylinder 21.
- the outer circumference of the second cylinder 22 is located at a more inward position than the screw hole of the fixing bolt 35, and hence the second cylinder 22 can easily be attached to the first cylinder 21.
- Each of the compressors K and Ka includes a suction hole (d) and a branch suction path (d1, e, f) shown in FIG. 2 .
- the suction hole (d) is formed in the first cylinder 21, and extends in the radial direction of the first cylinder chamber Sa.
- the branch suction path (d1, e, f) includes a branch hole (d1), suction guide hole (e), and guide groove (f).
- the suction guide hole (e) is formed in the intermediate partition plate 20, and penetrates the intermediate partition plate 20 in the vertical direction.
- the branch hole (d1) is formed in the first cylinder 21, and communicates with the suction hole (d) and suction guide hole (e).
- the guide groove (f) is formed in the second cylinder 22, and communicates with the second cylinder chamber Sb and suction guide hole (e).
- a distance from an upper end face of the second cylinder 22 to an end section of the compression element 12 is H1
- distance from a lower end face of the second cylinder 22 to the end section of the compression element 12 is H2
- radius of curvature of the corner part of the lower end case 10c is R.
- the end section of the compression element 12 is an undersurface of the valve cover 28.
- the compressors K and Ka of the first and second embodiments are configured to satisfy the condition H1>R>H2.
- the condition H1>R is satisfied, and hence an appropriate amount of lubricating oil can be retained in the lower end case 10c.
- Lubricating oil is supplied to slide components constituting the compression element 12, whereby the reliability of the compression element 12 can be secured.
- the condition R>H2 is satisfied, and hence it is possible to make the shape of the lower end case 10c more similar to a spherical shape, and enhance the pressure resistance. Accordingly, the rigidity of the hermetic case 10 can be secured without excessively increasing the wall thickness of the hermetic case 10. According to the compressors K and Ka of the first and second embodiments, it is possible to enhance the pressure resistance of the hermetic case 10 and prevent the hermetic case 10 from becoming larger in size.
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Abstract
Description
- Embodiments described herein relate generally to a hermetic rotary compressor and refrigeration cycle device provided with the hermetic rotary compressor.
- A hermetic rotary compressor is provided with a hermetic case configured to accommodate therein an electric motor section and compression mechanism section. The hermetic case is constituted of, for example, a cylindrical main case and lid-like end cases, and the end cases having an identical diameter are fitted into both ends of the main case to thereby hermetically seal the hermetic case. In
FIG. 1 of Patent Literature 1, a rotary compressor in which a hermetic case is hermetically sealed by inserting end cases having diameters smaller than an inner diameter of a main case into both ends of the main case is disclosed. A cylinder disclosed in Patent Literature 1 is formed smaller than an inner diameter of the end case. - In recent years, a carbon dioxide refrigerant has been brought into use as a working fluid of a refrigeration cycle device. A carbon dioxide refrigerant has working pressure higher than a hitherto used HFC-based refrigerant, and hence it is necessary to enhance the pressure resistance of the hermetic case. When a shape of a corner part of an end case is made more similar to a spherical shape in order to enhance the pressure resistance of the hermetic case, the end case is made larger in the axial direction, thereby upsizing the hermetic rotary compressor. In particular, in the case of a vertically-installed structure, when the hermetic case becomes larger in the axial direction, the quantity of oil to be sealed in the hermetic case is increased, thereby making the hermetic rotary compressor heavier. An increase in the oil quantity is not desirable from the viewpoint of running costs and natural resources saving.
- Patent Literature 1:
JP 3958443 B - Embodiments described herein aim to provide a hermetic rotary compressor capable of improving the pressure resistance of the hermetic case and restraining upsizing of the hermetic case, and refrigeration cycle device provided with the hermetic rotary compressor.
- According to one embodiment, a hermetic rotary compressor comprises a hermetic case, a rotating shaft, an electric motor section and a plurality of compression mechanism sections. The rotating shaft, the electric motor section and the compression mechanism sections are accommodated in the hermetic case. The electric motor section rotates the rotating shaft. The compression mechanism sections are coupled to the rotating shaft, and compress a working fluid. The compression mechanism sections include a first compression mechanism section and a second compression mechanism section. The first compression mechanism section is provided with a first cylinder, and the second compression mechanism section is provided with a second cylinder. The hermetic case is provided with a main case and end cases. The main case includes openings and the end cases are fitted into the openings. The whole of the first cylinder is positioned inside the main case in an axial direction of the rotating shaft, and at least part of the second cylinder is positioned inside the end case. The maximum distance from a center of the rotating shaft to an outer circumference of the first cylinder is greater than the maximum distance from the center of the rotating shaft to an inner circumference of the end case.
- A refrigeration cycle device of an embodiment is provided with the aforementioned hermetic rotary compressor and a refrigeration cycle circuit. In the refrigeration cycle circuit, a heat radiator, expanding device, and heat absorber are connected to each other in sequence, and a working fluid circulates through the circuit. The hermetic rotary compressor is connected to the refrigeration cycle circuit between the heat radiator and heat absorber.
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FIG. 1 is a cross-sectional view showing an example of a hermetic rotary compressor of a first embodiment. -
FIG. 2 is a cross-sectional view showing an example of a hermetic rotary compressor of a second embodiment. - Hereinafter, a hermetic rotary compressor of each of embodiments will be described with reference to
FIG. 1 andFIG. 2 .FIG. 1 is a cross-sectional view showing an example of a hermetic rotary compressor K of a first embodiment. Further,FIG. 1 also shows the configuration of a refrigeration cycle device provided with the hermetic rotary compressor K at the same time. In the following descriptions, the hermetic rotary compressor K will be simply referred to as a compressor K. - As shown in
FIG. 1 , the refrigeration cycle device includes, as major elements, a compressor K,heat radiator 2, expandingdevice 3, and heat absorber 4. Theheat radiator 2, expandingdevice 3, and heat absorber 4 are connected to each other in sequence through refrigerant pipes P. The compressor K is connected between theheat radiator 2 and heat absorber 4. An accumulator 5 is annexed to the compressor K. The major elements of the refrigeration cycle device constitute a refrigeration cycle circuit T through which the working fluid circulates. - The compressor K is provided with a
hermetic case 10,electric motor section 11, andcompression element 12 constituted of a plurality of compression mechanism sections, and rotatingshaft 13. Theelectric motor section 11 is an example of a driving element. Theelectric motor section 11 andcompression element 12 are accommodated in thehermetic case 10 and are coupled to each other through the rotatingshaft 13. - In the example shown in
FIG. 1 , the compressor K is configured as a vertical rotary compressor. It should be noted that the compressor K is not limited to the vertical type, and may also be a horizontal rotary compressor. In the description ofFIG. 1 , a direction from theelectric motor section 11 toward thecompression element 12 along the rotatingshaft 13 is called a "downward direction" or a "lower part" and, a direction opposite thereto is called an "upward direction" or an "upper part". Further, a length in the axial direction of the rotatingshaft 13 is simply referred to as a "height". - Inside the
hermetic case 10, lubricating oil is retained in an oil basin section Z located at a lowermost end, and the remaining space is filled with refrigerant gas serving as the working fluid. The compressor K of the first embodiment uses a carbon dioxide (CO2) refrigerant as the working fluid. The carbon dioxide refrigerant has working pressure higher than the HFC-based refrigerant. Accordingly, high pressure resistance is required of thehermetic case 10 of the compressor K. - The
hermetic case 10 is constituted of amain case 10a,lower end case 10c, andupper end case 10b. Themain case 10a is formed into a cylindrical shape both ends of which are opened. Thelower end case 10c is formed into a dish-like shape having an outer diameter smaller than an inner diameter of themain case 10a, and is fitted into a lower end of themain case 10a. Thelower end case 10c is an example of an end case. - The
upper end case 10b has a shape roughly identical to thelower end case 10c, and is fitted into an upper end of themain case 10a. Thelower end case 10c andupper end case 10b are coupled to the main case by welding or the like. It should be noted that themain case 10a andupper end case 10b may be formed integral with each other to thereby form a closed-end cylindrical configuration. Theupper end case 10b is another example of an end case. - In the hermetic rotary compressor K, a carbon dioxide refrigerant having high working pressure is used, and hence the
main case 10a,upper end case 10b, andlower end case 10c constituting thehermetic case 10 each have a heavy wall thickness. A wall thickness of a hermetic case using an HFC-based refrigerant is, for example, 3 to 4 mm. A wall thickness of thehermetic case 10 according to the first embodiment is, for example, 7 to 8 mm. - In the compressor K, each of the end cases of the
hermetic case 10 is not formed into a flat-plate shape, and is formed into a dish-like shape, and hence the pressure resistance thereof can be enhanced. The end cases are fitted into themain case 10a, and hence the end cases can be made compact in size. An outer diameter of the end case is smaller than an outer diameter of themain case 10a by twice the wall thickness. - A suction refrigerant pipe Pa and lead-out refrigerant pipe Pb are attached to the
hermetic case 10. The suction refrigerant pipe Pa penetrates themain case 10a to thereby make the inside and outside of thehermetic case 10 communicate with each other. The lead-out refrigerant pipe Pb penetrates theupper end case 10b to thereby make the inside and outside of thehermetic case 10 communicate with each other. The suction refrigerant pipe Pa is connected to theheat absorber 4 through the accumulator 5. The lead-out refrigerant pipe Pb is connected to theheat radiator 2. - The
electric motor section 11 is provided with astator 15 androtor 16. Therotor 16 is fixed to therotating shaft 13. Thestator 15 is fixed to an inner circumferential surface of thehermetic case 10. An inner circumferential surface of thestator 15 is opposed to an outer circumferential surface of therotor 16 with a slight gap held between them. - The
compression element 12 is positioned beneath theelectric motor section 11 serving as a driving element. Thecompression element 12 is provided with, for example, a firstcompression mechanism section 18A, secondcompression mechanism section 18B,intermediate partition plate 20,main bearing 23,sub-bearing 24, and valve covers 27 and 28. The first and secondcompression mechanism sections second cylinders - The
compression element 12 is an example of a plurality of compression mechanism sections. It should be noted that the number of compression mechanism sections is not limited to two cylinders. Thecompression element 12 may be of a multi-cylinder type including third and fourth compression mechanism sections in addition to the first and secondcompression mechanism sections - The
main bearing 23 is fixed to the inner circumferential surface of thehermetic case 10 by, for example, welding. Thevalve cover 27,main bearing 23,first cylinder 21,intermediate partition plate 20,second cylinder 22,sub-bearing 24, and valve cover 28 are laid one on top of another in sequence from theelectric motor section 11 side, and are fixed to each other by, for example, jointly fastening. - The
main bearing 23 andsub-bearing 24 rotatably support the rotatingshaft 13. The valve covers 27 and 28 cover themain bearing 23 andsub-bearing 24, respectively. An undersurface of the sub-bearing 24 is an example of an end section of thecompression element 12. - In the
first cylinder 21, a circular first cylinder chamber Sa interposed between themain bearing 23 andintermediate partition plate 20 is formed. In thesecond cylinder 22, a circular second cylinder chamber Sb interposed between theintermediate partition plate 20 andsub-bearing 24 is formed. Each of the first and second cylinder chambers Sa and Sb is formed into a shape having an identical diameter and height. - The rotating
shaft 13 includes first and second eccentric sections a and b protruding in directions perpendicular to the axial direction. The first and second eccentric sections a and b are arranged in such a manner as to be shifted from each other by, for example, 180° with respect to the center of therotating shaft 13.Cylindrical rollers - The first eccentric section a and
roller 25 are arranged in the first cylinder chamber Sa. The second eccentric section b androller 26 are arranged in the second cylinder chamber Sb. When therotating shaft 13 rotates, theroller 25 rolls in a state where theroller 25 is in contact with the first cylinder chamber Sa, androller 26 rolls in a state where theroller 26 is in contact with the second cylinder chamber Sb. - In the
first cylinder 21, a blade storing groove extending in a radial direction of the first cylinder chamber Sa is formed. In thesecond cylinder 22, a blade storing groove extending in a radial direction of the second cylinder chamber Sb is formed. In the blade storing grooves of the first andsecond cylinders blades - A tip end of the
blade 30 is in slidable contact with an outer circumferential surface of theroller 25 to thereby separate the first cylinder chamber Sa into two parts. Likewise, a tip end of theblade 32 is in slidable contact with an outer circumferential surface of theroller 26 to thereby separate the second cylinder chamber Sb into two parts. - In the blade storing groove of the
first cylinder 21, a horizontal hole configured to arrange therein acoil spring 31 is formed. A base end of theblade 30 is pressed against theroller 25 by thecoil spring 31. Thecoil spring 31 is an example of an elastically energizing member. - On the other hand, in the blade storing groove of the
second cylinder 22, no horizontal hole for arranging therein acoil spring 31 is formed. The blade storing groove of thesecond cylinder 22 communicates with the inside of thehermetic case 10. A base end of theblade 32 is pressed against theroller 26 by the pressure of the working fluid filling thehermetic case 10. - The
blade 30 of the firstcompression mechanism section 18A is provided with the elastically energizing member, and hence is pressed against theroller 25 at all times without being subject to the pressure inside thehermetic case 10. On the other hand, theblade 32 of the secondcompression mechanism section 18B is not pressed against theroller 26 immediately after starting of theelectric motor section 11 when the pressure inside thehermetic case 10 is low. When the pressure inside thehermetic case 10 is raised by the firstcompression mechanism section 18A, theblade 32 enters a state where theblade 32 is pressed against theroller 26. - The
second cylinder 22 has no need of space for arrangement of the elastically energizing member, and hence can be configured more compact in size than thefirst cylinder 21. In thesecond cylinder 22, a horizontal hole for arrangement of the elastically energizing member is not formed, and hence, although thesecond cylinder 22 is smaller than thefirst cylinder 21 in diameter, sufficient pressure resistance can be secured. - In the
first cylinder 21, a suction hole is formed. In the suction hole, the aforementioned suction refrigerant pipe Pa is inserted. The suction hole and inside of the second cylinder chamber Sb communicate with each other by a branch suction path. The suction hole and branch suction path will be described later with reference toFIG. 2 . - The working fluid to be supplied from the refrigeration cycle circuit T through the suction refrigerant pipe Pa is guided from the suction hole to the first cylinder chamber Sa, and is then guided from the branch suction path to the second cylinder chamber Sb. The working fluid is compressed by the first and second cylinder chambers Sa and Sb concomitantly with the rotation of the
rotating shaft 13. - The working fluid compressed by the first cylinder chamber Sa is discharged into the inside of
valve cover 27 through a discharge valve mechanism provided to themain bearing 23, and is then supplied to the inside of thehermetic case 10 from a discharge hole formed in thevalve cover 27. - The working fluid compressed by the second cylinder chamber Sb is discharged into the inside of the
valve cover 28 through a discharge valve mechanism provided to the sub-bearing 24. The inside of thevalve cover 28 communicates with the inside of thevalve cover 27 by a discharge gas guide passage penetrating themain bearing 23,first cylinder 21,intermediate partition plate 20,second cylinder 22, andsub-bearing 24. The working fluid discharged into the inside of thevalve cover 28 is supplied to the inside of thehermetic case 10 through the inside of thevalve cover 27. - As shown in
FIG. 1 , in the axial direction of therotating shaft 13, the whole of thefirst cylinder 21 is positioned inside themain case 10a. At least part of thesecond cylinder 22 is positioned inside thelower end case 10c. - The compressor K of the first embodiment is characterized in that the maximum distance L from the center of the
rotating shaft 13 to the outer circumference of thefirst cylinder 21 is greater than the maximum distance M from the center of therotating shaft 13 to the inner circumference of thelower end case 10c. Accordingly, the maximum distance L from the center of therotating shaft 13 to the outer circumference of thefirst cylinder 21 is greater than the maximum distance from the center of therotating shaft 13 to the outer circumference of thesecond cylinder 22. Thesecond cylinder 22 is formed more compact than thefirst cylinder 21 in size. - The compressor K of the first embodiment configured as described above is provided with the
compression element 12 constituted of a plurality of compression mechanism sections. Of the plurality of compression mechanism sections, the secondcompression mechanism section 18B is configured in such a manner that at least part of thesecond cylinder 22 thereof is positioned inside thelower end case 10c in the axial direction of therotating shaft 13. - When the shape of the
lower end case 10c is made more similar to a spherical shape in order to enhance the pressure resistance, the dimension of thelower end case 10c becomes larger in the axial direction of therotating shaft 13. However, in the first embodiment, at least part of thesecond cylinder 22 is positioned inside thelower end case 10c in the axial direction of therotating shaft 13. - According to the first embodiment, it is possible to allow at least part of the
second cylinder 22 to be positioned inside thelower end case 10c, and thereby form themain case 10a short, and hence it is possible to prevent thehermetic case 10 from becoming larger in size while enhancing the pressure resistance. - The
lower end case 10c according to the first embodiment is fitted into themain case 10a, and thelower end case 10c can be formed smaller in diameter than themain case 10a in the radial direction. In the first embodiment, even when thelower end case 10c is made larger in the axial direction, the oil basin section Z formed by thelower end case 10c does not become excessively large in the radial direction. - As a result, it is possible to prevent an excessive amount of lubricating oil from being retained in the oil basin section Z, and prevent the weight of the compressor K from increasing. It is possible to prevent the environmental load and running costs resulting from use of an excessive amount of lubricating oil from increasing. It is possible to contribute to downsizing and weight reduction of the compressor K.
- The second
compression mechanism section 18B according to the first embodiment utilizes the pressure inside thehermetic case 10 as means for pressing theblade 32. It is not necessary to form a horizontal hole configured to provide therein acoil spring 31 in thesecond cylinder 22 according to the first embodiment. - In the first embodiment, the horizontal hole making the rigidity the lowest in the cylinder is made unnecessary, and hence, even when the maximum distance from the center of the
rotating shaft 13 to the outer circumference of thesecond cylinder 22 is made small, the rigidity of thesecond cylinder 22 can be secured. Thesecond cylinder 22 can be formed small, and hence as described previously it is possible to configure a compressor K in which at least part of thesecond cylinder 22 is made inside thelower end case 10c. - In the first embodiment, of the plurality of compression mechanism sections, the first
compression mechanism section 18A is configured in such a manner that the whole of thefirst cylinder 21 is positioned inside themain case 10a in the axial direction of therotating shaft 13, and thus the outer diameter of thefirst cylinder 21 can be made larger than the inner circumference of thelower end case 10c. - When the pressure inside the
hermetic case 10 is utilized as means for pressing theblade 32, of the plurality of compression mechanism sections, at least one cylinder should be provided with ablade 30 pressed by an elastically energizing member. The horizontal hole storing therein the elastically energizing member is the part at which the rigidity is the lowest in the cylinder. - Further, of the plurality of compression mechanism sections, at least one cylinder is connected to the suction refrigerant pipe Pa penetrating the cylinder. The suction hole (d) in which the suction refrigerant pipe Pa is to be inserted is the part at which the rigidity is the lowest in the cylinder as in the case of the horizontal hole configured to store therein the elastically energizing member.
- In the first embodiment, the horizontal hole and suction hole (d) are formed in only the
first cylinder 21 having a sufficient wall thickness, and these holes are not formed in another cylinder. According to the first embodiment, it is possible to form thefirst cylinder 21 larger in the radial direction, and secure a sufficient wall thickness. Accordingly, even when the horizontal hole and suction hole (d) are formed in thefirst cylinder 21, rigidity can be secured to thefirst cylinder 21. - Next, a compressor Ka of a second embodiment will be described below with reference to
FIG. 2. FIG. 2 is a cross-sectional view showing an example of a hermetic rotary compressor Ka of a second embodiment. In the second embodiment, the configuration of amain bearing 23 differs from themain bearing 23 of the first embodiment. Other configurations are identical to the first embodiment. Configurations having functions identical to or similar to the configurations described in the first embodiment are denoted by reference symbols identical to the first embodiment to thereby enable reference to corresponding descriptions of the first embodiment, and duplicated descriptions are omitted. - In the compressor Ka of the second embodiment, a
main bearing 23 is divided intoframes frame 230a is fixed to an inner circumferential surface of ahermetic case 10 by, for example, welding. Theframe 230b is fixed to theframe 230a by means of a fixingbolt 35, and rotatably supports arotating shaft 13. - When the compressor Ka is to be assembled, first the
frame 230a is fixed to the inner circumferential surface of themain case 10a as a single item. Subsequently, theframe 230b in a state where first andsecond cylinders frame 230a. Themain bearing 23 is divided into theframes frame 230a with respect to themain case 10a. - As described previously with reference to
FIG. 1 , thefirst cylinder 21 is formed in such a manner that the maximum distance L from the center of therotation shaft 13 to the outer circumference of thefirst cylinder 21 is made larger than the maximum distance M from the center of therotating shaft 13 to the inner circumference of thelower end case 10c. Thefirst cylinder 21 is sufficiently large in size, and hence even when a screw hole for fastening by the fixingbolt 35 is formed therein, the rigidity of thefirst cylinder 21 can be secured. - As described previously, the
second cylinder 22 is formed smaller than thefirst cylinder 21. The outer circumference of thesecond cylinder 22 is located at a more inward position than the screw hole of the fixingbolt 35, and hence thesecond cylinder 22 can easily be attached to thefirst cylinder 21. - Subsequently, a configuration common to the first and second embodiments will be described below in more detail. Each of the compressors K and Ka includes a suction hole (d) and a branch suction path (d1, e, f) shown in
FIG. 2 . The suction hole (d) is formed in thefirst cylinder 21, and extends in the radial direction of the first cylinder chamber Sa. - The branch suction path (d1, e, f) includes a branch hole (d1), suction guide hole (e), and guide groove (f). The suction guide hole (e) is formed in the
intermediate partition plate 20, and penetrates theintermediate partition plate 20 in the vertical direction. The branch hole (d1) is formed in thefirst cylinder 21, and communicates with the suction hole (d) and suction guide hole (e). The guide groove (f) is formed in thesecond cylinder 22, and communicates with the second cylinder chamber Sb and suction guide hole (e). - As shown in
FIG. 2 , it is assumed that a distance from an upper end face of thesecond cylinder 22 to an end section of thecompression element 12 is H1, distance from a lower end face of thesecond cylinder 22 to the end section of thecompression element 12 is H2, and radius of curvature of the corner part of thelower end case 10c is R. In the example shown inFIG. 2 , the end section of thecompression element 12 is an undersurface of thevalve cover 28. The compressors K and Ka of the first and second embodiments are configured to satisfy the condition H1>R>H2. - Assuming that the compressors K and Ka are configured to satisfy the condition H1<R, the amount of lubricating oil retainable in the
lower end case 10c decreases to an extreme, and there is a fear that a shortage of lubricating oil will be caused to thecompression element 12. Assuming that the compressors K and Ka are configured to satisfy the condition H2>R, the pressure resistance of thelower end case 10c is lowered. - Conversely, in the first and second embodiments, the condition H1>R is satisfied, and hence an appropriate amount of lubricating oil can be retained in the
lower end case 10c. Lubricating oil is supplied to slide components constituting thecompression element 12, whereby the reliability of thecompression element 12 can be secured. - Moreover, in the first and second embodiments, the condition R>H2 is satisfied, and hence it is possible to make the shape of the
lower end case 10c more similar to a spherical shape, and enhance the pressure resistance. Accordingly, the rigidity of thehermetic case 10 can be secured without excessively increasing the wall thickness of thehermetic case 10. According to the compressors K and Ka of the first and second embodiments, it is possible to enhance the pressure resistance of thehermetic case 10 and prevent thehermetic case 10 from becoming larger in size. - 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.
- 2 ··· heat radiator, 3 ··· expanding device, 4 ··· heat absorber, 10 ··· hermetic case, 11 ··· electric motor section, 12 ··· compression element (example of a plurality of compression mechanism sections), 13 ... rotating shaft, 18A ··· first compression mechanism section, 18B ··· second compression mechanism section, 10a ··· main case, 10c ··· lower end case, 21 ··· first cylinder, 22 ··· second cylinder, 25, 26 ··· roller, 28 ··· valve cover (example of an end section of a plurality of compression mechanism sections), 30, 32 ··· blade, 31 ··· coil spring (example of an elastically energizing member), d ··· suction hole, d1, e, f ··· branch suction path, H1 ··· distance from an upper end face of the second cylinder to an end section of a plurality of compression mechanism sections, H2 ··· distance from a lower end face of the second cylinder to the end section of the plurality of compression mechanism sections, K ··· hermetic rotary compressor, L ··· maximum distance from the center to the outer circumference of the first cylinder, M ··· maximum distance from the center to the inner circumference of the end case, Pa ··· suction refrigerant pipe, R ··· radius of curvature of the corner part of the end case, and T ··· refrigeration cycle circuit.
Claims (7)
- A hermetic rotary compressor characterized by comprising:a hermetic case;a rotating shaft accommodated in the hermetic case;an electric motor section accommodated in the hermetic case and configured to rotate the rotating shaft; anda plurality of compression mechanism sections accommodated in the hermetic case, coupled to the rotating shaft, and configured to compress a working fluid, whereinthe plurality of compression mechanism sections include a first compression mechanism section provided with a first cylinder, and a second compression mechanism section provided with a second cylinder,the hermetic case is provided with a main case including openings and end cases fitted into the openings,the whole of the first cylinder is positioned inside the main case in an axial direction of the rotating shaft, and at least part of the second cylinder is positioned inside the end case, andthe maximum distance from a center of the rotating shaft to an outer circumference of the first cylinder is greater than the maximum distance from the center of the rotating shaft to an inner circumference of the end case.
- The hermetic rotary compressor of Claim 1, characterized in that
each of the plurality of compression mechanism sections is provided with a roller fitted on the rotating shaft and configured to compress the working fluid, and a blade in contact with the roller and dividing the working fluid into two parts, and
although the first cylinder is provided with an elastically energizing member configured to press the blade against the roller, the second cylinder is not provided with an elastically energizing member. - The hermetic rotary compressor of Claim 1, characterized by further comprising a suction refrigerant pipe penetrating the main case, and making the inside and the outside of the hermetic case communicate with each other, wherein
the suction refrigerant pipe is not inserted into the second compression mechanism section, and is inserted into the first compression mechanism section. - The hermetic rotary compressor of Claim 3, characterized by further comprising:a suction hole which is formed in the first cylinder and into which the suction refrigerant pipe is inserted; anda branch suction path formed between the first compression mechanism section and the second compression mechanism section, and making the suction hole and the inside of the second cylinder communicate with each other.
- The hermetic rotary compressor of Claim 1, characterized in that
a radius of curvature of a corner part of the end case is smaller than a distance from one end face of the second cylinder to an end section of the plurality of compression mechanism sections, and is greater than a distance from the other end face of the second cylinder to the end section of the plurality of compression mechanism sections. - The hermetic rotary compressor of Claim 1, characterized in that
the working fluid is a carbon dioxide refrigerant. - A refrigeration cycle device comprising:a refrigeration cycle circuit in which a heat radiator, an expanding device, and a heat absorber are connected to each other in sequence and through which a working fluid circulates; andthe hermetic rotary compressor of any one of Claims 1 to 6 connected to the refrigeration cycle circuit between the heat radiator and the heat absorber.
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JP2016062296 | 2016-03-25 | ||
PCT/JP2017/011063 WO2017164138A1 (en) | 2016-03-25 | 2017-03-17 | Hermetic rotary compressor and refrigeration cycle device |
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EP3434902A4 EP3434902A4 (en) | 2019-10-02 |
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JP (1) | JP6574519B2 (en) |
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JPH0410392Y2 (en) * | 1985-07-29 | 1992-03-13 | ||
JPH03271590A (en) * | 1990-03-20 | 1991-12-03 | Matsushita Refrig Co Ltd | Rotary compressor |
JPH05106575A (en) * | 1991-08-23 | 1993-04-27 | Hitachi Ltd | Multi-cylinder rotary compressor |
JPH062678A (en) * | 1992-06-22 | 1994-01-11 | Mitsubishi Electric Corp | Closed type rotary compressor |
JPH10266984A (en) * | 1997-03-26 | 1998-10-06 | Toshiba Corp | Rotary compressor |
JPH10318170A (en) * | 1997-05-20 | 1998-12-02 | Toshiba Corp | Compressor |
JPH11336682A (en) * | 1998-05-26 | 1999-12-07 | Toshiba Corp | Compressor |
JP4634191B2 (en) * | 2005-03-04 | 2011-02-16 | 東芝キヤリア株式会社 | Hermetic compressor and refrigeration cycle apparatus |
WO2007023904A1 (en) * | 2005-08-25 | 2007-03-01 | Toshiba Carrier Corporation | Hermetic compressor and refrigeration cycle device |
KR101381085B1 (en) * | 2007-11-13 | 2014-04-10 | 엘지전자 주식회사 | 2 stage rotary compressor |
CN101169117A (en) * | 2007-11-17 | 2008-04-30 | 美的集团有限公司 | Air suction device of capacity control rotary compressor |
JP6045468B2 (en) * | 2013-09-27 | 2016-12-14 | 三菱重工業株式会社 | Rotary compressor |
CN104632581B (en) * | 2014-11-28 | 2017-02-01 | 珠海格力节能环保制冷技术研究中心有限公司 | Double-cylinder two-stage compressor and air conditioner system |
CN105221423B (en) * | 2015-10-21 | 2018-06-12 | 安徽美芝精密制造有限公司 | Horizontal compressor |
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JP6574519B2 (en) | 2019-09-11 |
EP3434902B1 (en) | 2020-10-07 |
WO2017164138A1 (en) | 2017-09-28 |
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