EP3434902B1 - Hermetischer drehkompressor und kühlkreisvorrichtung - Google Patents

Hermetischer drehkompressor und kühlkreisvorrichtung Download PDF

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Publication number
EP3434902B1
EP3434902B1 EP17770180.2A EP17770180A EP3434902B1 EP 3434902 B1 EP3434902 B1 EP 3434902B1 EP 17770180 A EP17770180 A EP 17770180A EP 3434902 B1 EP3434902 B1 EP 3434902B1
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EP
European Patent Office
Prior art keywords
cylinder
case
hermetic
rotating shaft
refrigerant
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EP17770180.2A
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English (en)
French (fr)
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EP3434902A4 (de
EP3434902A1 (de
Inventor
Takuya Hirayama
FERDHY Monasry JAFET
Shinya Goto
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Toshiba Carrier Corp
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Toshiba Carrier Corp
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Publication of EP3434902A4 publication Critical patent/EP3434902A4/de
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Classifications

    • 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.
  • JP H11 336682 A discloses a rotary compression mechanism with a helical blade. Rotation is transmitted to a roller by a rotating shaft. A blade inserted inside a helical groove is abutted against the roller, partitioning the compression chamber. In FIG. 7, a two stage compressor with two compression chambers is disclosed.
  • WO 2009/064042 A1 discloses a two stage rotary compressor including a low pressure compression assembly, a middle plate and a high pressure compression assembly.
  • CN 104 632 581 A discloses a two stage compressor comprising a housing with an upper and a lower cover, wherein an outlet pipe is connected with the upper cover.
  • 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.
  • 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 is provided with the features according to claim 1.
  • 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 the main case 10a of a hermetic case 10 by, for example, welding.
  • the frame 230a is stacked on the outer circumferential portion of the first cylinder 21 and fixed to the first cylinder 21 via a fixing bolt 35a.
  • the frame 230b is surrounded by the frame 230a and is located on the first cylinder 21. Further, the frame 230b is fixed to the first cylinder 21 via a fixing bolt 35b, 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 bolts 35a and 35b is formed in the first cylinder 21, 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 35a, 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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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (4)

  1. Hermetischer Rotationsverdichter aufweisend:
    ein hermetisches Gehäuse (10), das ein Hauptgehäuse (10a) mit einer Öffnung aufweist und eine Zylinderform hat, und ein Endgehäuse (10c) umfasst, das in das Innere der Öffnung des Hauptgehäuses (10a) eingesetzt ist und aus der Öffnung nach außerhalb des Hauptgehäuses (10a) hervorsteht, und in dem Schmieröl gespeichert ist;
    eine Drehwelle (13), die in dem hermetischen Gehäuse (10) untergebracht ist;
    einen Elektromotorenabschnitt (11), der in dem hermetischen Gehäuse (10) untergebracht und so konfiguriert ist, dass er die Drehwelle (13) dreht;
    ein Ansaug-Kältemittelrohr (Pa), dass das Hauptgehäuse (10a) durchdringt und die Innen- und Außenseite des hermetischen Gehäuses (10)miteinander in Verbindung bringt und dem ein Kältemittel zugeführt wird; und
    einem Verdichterelement (12), das in dem hermetischen Gehäuse (10) untergebracht, mit der Drehwelle (13) gekoppelt und so konfiguriert ist, dass es das von dem Ansaug-Kältemittelrohr (Pa) zugeführte Kältemittel verdichtet, wobei das Verdichtungselement umfasst:
    einen ersten Verdichtungsmechanismusabschnitt (18A), der einen ersten Zylinder (21) mit einer ersten Zylinderkammer (Sa), ein Ansaugloch (d), das in dem ersten Zylinder (21) ausgebildet und mit der ersten Zylinderkammer (Sa) verbunden ist, und in das das Ansaug-Kältemittelrohr (Pa) eingeführt ist, eine Walze (25), die auf der Drehwelle (13) angebracht und so konfiguriert ist, dass sie das Kältemittel in der ersten Zylinderkammer verdichtet, und ein Blatt (30) umfasst, das mit der Walze in Kontakt steht und das Kältemittel in der ersten Zylinderkammer in zwei Teile aufteilt, und
    einen zweiten Verdichtungsmechanismusabschnitt (18B), der einen zweiten Zylinder (22) mit einer zweiten Zylinderkammer (Sb), einer Walze (26), die auf der Drehwelle (13) angebracht und so konfiguriert ist, dass sie das Kältemittel in der zweiten Zylinderkammer verdichtet, und ein Blatt (32) umfasst, das mit der Walze (26) in Kontakt steht und das Kältemittel in der zweiten Zylinderkammer in zwei Teile aufteilt, wobei der zweite Verdichtungsmechanismusabschnitt (18B) angrenzend an den ersten Verdichtungsmechanismusabschnitt (18A) in einer axialen Richtung der Drehwelle (13) vorgesehen ist; und
    der gesamte erste Zylinder (21) in dem Inneren des Hauptgehäuses (10a) in axialer Richtung der Drehwelle (13) angeordnet ist, und zumindest ein Teil des zweiten Zylinders (22) im Inneren des Endgehäuses angeordnet ist, und
    ein maximaler Abstand (L) von einem Mittelpunkt der Drehwelle (13) zu einem Außenumfang des ersten Zylinders größer ist als ein maximaler Abstand (M) von dem Mittelpunkt der Drehwelle zu einem Innenumfang des Endgehäuses, und
    dadurch gekennzeichnet, dass
    das Blatt (30) des ersten Zylinders (21) mittels eines elastischen Energieelementes (31) gegen die Walze (25) gedrückt wird, das in dem ersten Zylinder (21) vorgesehen ist, und das Blatt (32) des zweiten Zylinders (22) durch den Druck des Kältemittels im Inneren des hermetischen Gehäuses (10) gegen die Walze (26) gedrückt wird und
    ein Abzweigsaugpfad (d) zwischen dem ersten Verdichtungsmechanismusabschnitt (18A) und dem zweiten Verdichtungsmechanismusabschnitt (18B) gebildet wird, wobei das Ansaugloch (d) des ersten Zylinders (21) und die zweite Zylinderkammer (Sb) des zweiten Zylinders (22) miteinander verbunden werden.
  2. Hermetischer Rotationsverdichter nach Anspruch 1, dadurch gekennzeichnet, dass er geeignet ist, mit Kohlendioxid als Kältemittel betrieben zu werden.
  3. Hermetischer Rotationsverdichter nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass ein Krümmungsradius (R) eines Eckteils des Endgehäuses kleiner ist als ein Abstand (H1) einer Stirnfläche des Verdichtungselements (2) und größer als ein Abstand (H2) der anderen Stirnfläche des zweiten Zylinders zum Endabschnitt des Verdichterelements.
  4. Eine Kältekreislaufvorrichtung aufweisend:
    einen Kältekreislauf (T), in dem ein Wärmestrahler (2), eine Expansionsvorrichtung (3) und Wärmeabsorber (4) in Reihe miteinander verbunden sind, und durch den das Kohlendioxid-Kältemittel zirkuliert; und dadurch gekennzeichnet, dass
    der hermetische Rotationsverdichter nach einem der Ansprüche 2 oder 3 verbunden ist mit dem Kältekreislauf (T) zwischen dem Wärmestrahler (2) und dem Wärmeabsorber (4) angeschlossen ist.
EP17770180.2A 2016-03-25 2017-03-17 Hermetischer drehkompressor und kühlkreisvorrichtung Active EP3434902B1 (de)

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JP2016062296 2016-03-25
PCT/JP2017/011063 WO2017164138A1 (ja) 2016-03-25 2017-03-17 密閉型ロータリ圧縮機及び冷凍サイクル装置

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JPH0410392Y2 (de) * 1985-07-29 1992-03-13
JPH03271590A (ja) * 1990-03-20 1991-12-03 Matsushita Refrig Co Ltd 回転式圧縮機
JPH05106575A (ja) * 1991-08-23 1993-04-27 Hitachi Ltd 複数シリンダロータリ圧縮機
JPH062678A (ja) * 1992-06-22 1994-01-11 Mitsubishi Electric Corp 密閉型回転圧縮機
JPH10266984A (ja) * 1997-03-26 1998-10-06 Toshiba Corp ロータリコンプレッサ
JPH10318170A (ja) * 1997-05-20 1998-12-02 Toshiba Corp コンプレッサ
JPH11336682A (ja) * 1998-05-26 1999-12-07 Toshiba Corp 圧縮機
JP4634191B2 (ja) * 2005-03-04 2011-02-16 東芝キヤリア株式会社 密閉形圧縮機および冷凍サイクル装置
JP4769811B2 (ja) * 2005-08-25 2011-09-07 東芝キヤリア株式会社 密閉型圧縮機及び冷凍サイクル装置
KR101381085B1 (ko) * 2007-11-13 2014-04-10 엘지전자 주식회사 로터리식 2단 압축기
CN101169117A (zh) * 2007-11-17 2008-04-30 美的集团有限公司 容量控制旋转式压缩机的吸气装置
JP6045468B2 (ja) * 2013-09-27 2016-12-14 三菱重工業株式会社 ロータリ圧縮機
CN104632581B (zh) * 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 双缸两级压缩机和空调系统
CN105221423B (zh) * 2015-10-21 2018-06-12 安徽美芝精密制造有限公司 卧式压缩机

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EP3434902A4 (de) 2019-10-02
JP6574519B2 (ja) 2019-09-11
EP3434902A1 (de) 2019-01-30
CN109072916B (zh) 2021-04-02
WO2017164138A1 (ja) 2017-09-28
CN109072916A (zh) 2018-12-21
JPWO2017164138A1 (ja) 2018-08-09

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