EP3617514B1 - Zweistufig verdichtender kompressor, vom typ interner mittlerer druck - Google Patents

Zweistufig verdichtender kompressor, vom typ interner mittlerer druck Download PDF

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Publication number
EP3617514B1
EP3617514B1 EP18790603.7A EP18790603A EP3617514B1 EP 3617514 B1 EP3617514 B1 EP 3617514B1 EP 18790603 A EP18790603 A EP 18790603A EP 3617514 B1 EP3617514 B1 EP 3617514B1
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EP
European Patent Office
Prior art keywords
compression mechanism
compression
cylinder
stage
vane
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Application number
EP18790603.7A
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English (en)
French (fr)
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EP3617514A4 (de
EP3617514A1 (de
Inventor
Akira Matsuzaki
Takashi Sato
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Panasonic Intellectual Property Management Co Ltd
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Panasonic Intellectual Property Management Co Ltd
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Publication of EP3617514A1 publication Critical patent/EP3617514A1/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
    • F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
    • F04B37/12—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use to obtain high pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation

Definitions

  • the present invention relates to an internal medium pressure type two-stage compression compressor which is suitable especially when carbon dioxide is used as refrigerant.
  • Patent document 1 discloses an internal medium pressure type two-stage compression compressor.
  • a through hole is formed in an intermediate partition plate.
  • oil is pumped up from an oil reservoir in a bottom in an airtight container, the oil rises through an in-shaft oil supply passage and comes out from the in-shaft oil supply passage, the oil enters the through hole of the intermediate partition plate, the oil passes there, and the oil is supplied toward a low pressure chamber (suction side) of a high-stage side cylinder.
  • Inner pressure (suction pressure) in the low pressure chamber of the high-stage side cylinder becomes lower than pressure on the side of an inner peripheral edge of the intermediate partition plate by suction pressure loss in suction process.
  • suction pressure oil in the high-stage side cylinder is injected from the in-shaft oil supply passage into the low pressure chamber in the high-stage side cylinder through the through hole of the intermediate partition plate, and the oil is supplied.
  • Patent document 2 discloses an internal intermediate pressure multistage compression type rotary compressor.
  • a lubrication groove for providing communication between an oil bore and a low-pressure chamber in a cylinder is formed in a surface of an intermediate partitioner that is adjacent to the cylinder of a second rotary compressing element.
  • a through bore for providing communication between a hermetically sealed vessel and an inside of a roller is formed in the intermediate partitioner.
  • Patent document 3 discloses a rotary compressor, wherein a roller is fitted between an upper cylinder constituting a second rotary compression element and an eccentric portion formed on a rotary shaft of an electric element so as to rotate eccentrically in the upper cylinder.
  • a vane is brought in contact with the roller to divide the upper cylinder into a low pressure chamber and a high pressure chamber.
  • a back pressure chamber is defined to apply back pressure to the vane.
  • a back pressure passage is defined to interconnect the high pressure chamber in the upper cylinder and the back pressure chamber.
  • a check valve is disposed in the back pressure passage to permit a flow of gas from the high pressure chamber in the upper cylinder to the back pressure chamber and to block a flow of gas from the back pressure chamber to the high pressure chamber in the upper cylinder.
  • Patent document 4 discloses a rolling-piston type compressor, wherein a direction of an intake port for an inner surface of a cylinder is varied without varying a position of an opening of the intake port on an inner surface of the cylinder. Therefore, the shape of the intake port on the inner surface of the cylinder is changed to an elliptical form from its original circular form, and the area of the intake port is increased. Further, the intake port is continuous to the sliding groove on a partitioning plate so that a perfect closing of the intake port by a rotor is prevented.
  • Patent document 5 discloses a rotary compressor.
  • Fig. 4(a) is a plan view of essential portions of a compression mechanism on the high-stage side of the internal medium pressure type two-stage compression compressor as disclosed in patent document 1.
  • Fig. 4(b) is an enlarged plan view of essential portions of Fig. 4(a) .
  • the compression mechanism 100 includes a cylinder 101, a piston 102 placed in the cylinder 101 and a vane 103 which divides an interior of the cylinder 101.
  • an oil supply passage 105 is formed in a suction passage 104 of the compression mechanism 100.
  • the closed space 106 is in a negative pressure state, the piston 102 turns to the position of the suction passage 104, and if the closed space 106 comes into communication with the suction passage 104, suction pressure in the suction passage 104 is lowered by the closed space 106.
  • an object of the present invention to provide an internal medium pressure type two-stage compression compressor capable of preventing lubricant oil from flowing into a high-stage side compression chamber more than a set value.
  • the object is achieved by providing an internal medium pressure type two-stage compression compressor as defined in appended claim 1.
  • the internal medium pressure type two-stage compression compressor of the present invention comprises a motor and a compression mechanism in an airtight container, in which the motor and the compression mechanism are connected to each other through a shaft, the compression mechanism includes a cylinder, a piston placed in the cylinder and a vane for partitioning an interior of the cylinder, the compression mechanism includes a first compression mechanism which carries out first stage low stage compression, and a second compression mechanism which carries out second stage high stage compression, an oil supply passage is formed in a suction passage of the second compression mechanism, refrigerant gas which is compressed by the first compression mechanism is discharged into the airtight container, the refrigerant gas is compressed by the second compression mechanism and discharged outside the airtight container, and oil is supplied to a second compression chamber of the second compression mechanism from the oil supply passage by a pressure difference between case internal pressure in the airtight container and suction pressure in the suction passage of the second compression mechanism, wherein when the piston turns from a top dead center to a position of the suction passage, a closed
  • a pressure communication groove is formed in a vane-side wall surface located on a side of the vane of the suction passage.
  • the pressure communication groove is formed from an arc surface centering on a phantom center axis which is parallel to a center axis of the shaft.
  • the arc surface is formed from one of end surfaces to an other end surface of the cylinder.
  • a curved surface having a same curvature as the arc surface centering on the phantom center axis is formed on an anti-vane-side wall surface which is opposed to the vane-side wall surface.
  • a lower end of the shaft includes an oil pickup, an in-shaft oil supply passage through which lubricant oil pumped up by the oil pickup passes is formed in the shaft, an intermediate partition plate is provided between the first compression mechanism and the second compression mechanism, and an in-intermediate partition plate oil supply passage which introduces the lubricant oil of the in-shaft oil supply passage to the oil supply passage is formed in the intermediate partition plate.
  • carbon dioxide is used as refrigerant which is compressed by the compression mechanism.
  • the present invention it is possible to prevent lubricant oil from flowing into a second compression chamber more than a set value, and suppress a discharge amount of lubricant oil from the second compression chamber.
  • a closed space is not formed between a vane, a cylinder and the piston.
  • a pressure communication groove is formed in a vane-side wall surface located on a side of the vane of the suction passage.
  • the pressure communication groove is formed from an arc surface centering on a phantom center axis which is parallel to a center axis of the shaft.
  • the arc surface is formed from one of end surfaces to an other end surface of the cylinder.
  • the pressure communication groove can be formed by a rotary cutting processing.
  • a curved surface having a same curvature as the arc surface centering on the phantom center axis is formed on an anti-vane-side wall surface which is opposed to the vane-side wall surface.
  • a lower end of the shaft includes an oil pickup, an in-shaft oil supply passage through which lubricant oil pumped up by the oil pickup passes is formed in the shaft, an intermediate partition plate is provided between the first compression mechanism and the second compression mechanism, and an in-intermediate partition plate oil supply passage which introduces the lubricant oil of the in-shaft oil supply passage to the oil supply passage is formed in the intermediate partition plate.
  • carbon dioxide is used as refrigerant which is compressed by the compression mechanism.
  • carbon dioxide having high refrigerant pressure and having a large pressure difference between suction and discharge is used as refrigerant, since internal pressure of the airtight container is set to medium pressure. Therefore, it is possible to thin a thickness of the airtight container, the airtight container can be reduced in size and weight, and since a pressure difference per one stage is reduced. Hence, volumetric efficiency is enhanced.
  • Fig. 1 is a sectional view of an internal medium pressure type two-stage compression compressor according to the embodiment
  • Fig. 2 is an enlarged sectional view of essential portions of Fig. 1 .
  • the internal medium pressure type two-stage compression compressor of the embodiment includes a motor 20 and a compression mechanism 30 in an airtight container 10.
  • the motor 20 and the compression mechanism 30 are connected to each other through a shaft 40.
  • the motor 20 is composed of a stator 21 fixed to an inner surface of the airtight container 10 and a rotor 22 which rotates in the stator 21.
  • the internal medium pressure type two-stage compression compressor of the embodiment includes, as the compression mechanism 30, a first compression mechanism 30A which carries out first stage low stage compression, and a second compression mechanism 30B which carries out second stage high stage compression.
  • the first compression mechanism 30A includes a first cylinder 31A, a first piston 32A placed in the first cylinder 31A, and a vane (not shown) which partitions an interior of the first cylinder 31A. If the first piston 32A orbits in the first cylinder 31A, low pressure refrigerant gas is sucked and compressed.
  • the second compression mechanism 30B includes a second cylinder 31B, a second piston 32B placed in the second cylinder 31B, and a vane 33 (see Fig. 3(a) ) which partitions an interior of the second cylinder 31B. If the second piston 32B orbits in the second cylinder 31B, medium pressure refrigerant gas is sucked and compressed.
  • a lower bearing 51 is placed on one of surfaces of the first cylinder 31A, and an intermediate partition plate 52 is placed on the other surface of the first cylinder 31A.
  • the intermediate partition plate 52 is placed on one of surfaces of the second cylinder 31B, and an upper bearing 53 is placed on the other surface of the second cylinder 31B.
  • the intermediate partition plate 52 partitions into the first cylinder 31A and the second cylinder 31B.
  • the intermediate partition plate 52 has an opening which is larger than a diameter of the shaft 40.
  • the shaft 40 is composed of a main bearing 41 which mounts the rotor 22 and which is supported by the lower bearing 51, a first eccentric core 42 which mounts the first piston 32A, a second eccentric core 43 which mounts the second piston 32B, and an auxiliary bearing 44 which is supported by the lower bearing 51.
  • the first eccentric core 42 and the second eccentric core 43 are formed such that phases thereof are different from each other 180°, and a connecting shaft 45 is formed between the first eccentric core 42 and the second eccentric core 43.
  • a first compression chamber 34A is formed between an inner peripheral surface of the first cylinder 31A and an outer peripheral surface of the first piston 32A between the lower bearing 51 and the intermediate partition plate 52.
  • a second compression chamber 34B is formed between an inner peripheral surface of the second cylinder 31B and an outer peripheral surface of the second piston 32B between the intermediate partition plate 52 and the upper bearing 53.
  • An excluded volume ratio of high pressure compression excluded volume of the second compression mechanism 30B to low pressure compression excluded volume of the first compression mechanism 30A is set to 5% to 110%.
  • An oil reservoir 11 is formed in a bottom in the airtight container 10, and a lower end of the shaft 40 is provided with an oil pickup 12.
  • An in-shaft oil supply passage 46 is formed in the shaft 40 in its axial direction.
  • a communication passage 47 for supplying oil to a sliding surface of the compression mechanism 30 is formed in the in-shaft oil supply passage 46.
  • the communication passage 47 is formed in the first eccentric core 42 and the second eccentric core 43.
  • An oil supply passage 36 is formed in a suction passage 35B of the second compression mechanism 30B.
  • An in-intermediate partition plate oil supply passage 60 for introducing lubricant oil of the in-shaft oil supply passage 46 to the oil supply passage 36 is formed in the intermediate partition plate 52.
  • the in-intermediate partition plate oil supply passage 60 is composed of a first passage 61 extending from an inner peripheral surface 52a to an outer peripheral surface 52b of the intermediate partition plate 52, and a second passage 62 whose one end opens into the first passage 61 and whose other end opens into the oil supply passage 36.
  • a first intake tube 13A and a second intake tube 13B are connected to a side surface of the airtight container 10, and an intermediate pressure discharge tube 14 and a discharge tube (not shown) are connected to the airtight container 10.
  • the intermediate pressure discharge tube 14 is connected to an intermediate pressure discharge port 15.
  • the first intake tube 13A is connected to a suction passage 35A of the first compression mechanism 30A, and a second intake tube 13B is connected to the suction passage 35B of the second compression mechanism 30B.
  • the suction passage 35A is connected to the first compression chamber 34A, and the suction passage 35B is connected to the second compression chamber 34B.
  • the intermediate pressure discharge tube 14 is connected to an intercooler 16 which cools medium pressure refrigerant gas, and the intercooler 16 is connected to the second intake tube 13B.
  • a lower portion of the lower bearing 51 is provided with a cup muffler 71, and an upper portion of the upper bearing 53 is provided with an upper cover 72.
  • a first silencing chamber 81 is formed between the lower bearing 51 and the cup muffler 71, and a second silencing chamber 82 is formed between the upper bearing 53 and the upper cover 72.
  • the first piston 32A and the second piston 32B orbit in the first compression chamber 34A and the second compression chamber 34B by rotation of the shaft 40.
  • Gas refrigerant sucked from the first intake tube 13A into the first compression chamber 34A through the suction passage 35A is compressed by the first compression chamber 34A and then, the gas refrigerant is discharged into the first silencing chamber 81 by orbiting motion of the first piston 32A.
  • Medium pressure refrigerant gas discharged into the first silencing chamber 81 is discharged into the airtight container 10 through the lower bearing 51, the first cylinder 31A, the intermediate partition plate 52, the second cylinder 31B and a refrigerant passage (not shown) formed in the upper bearing 53.
  • the medium pressure refrigerant gas discharged into the airtight container 10 is introduced from the intermediate pressure discharge port 15 into the intermediate pressure discharge tube 14, the medium pressure refrigerant gas is further cooled by the intercooler 16 and then, the refrigerant gas is introduced into the second intake tube 13B.
  • Gas refrigerant sucked from the second intake tube 13B into the second compression chamber 34B through the suction passage 35B by the orbiting motion of the second piston 32B is compressed by the second compression chamber 34B and then, the gas refrigerant is discharged into the second silencing chamber 82.
  • High pressure refrigerant gas discharged into the second silencing chamber 82 is discharged outside the airtight container 10 from the discharge tube (not shown).
  • Lubricant oil sucked from the oil reservoir 11 by rotation of the shaft 40 is supplied from the communication passage 47 into the compression mechanism 30, and lubricates a sliding surface of the compression mechanism 30.
  • a portion of lubricant oil supplied from the communication passage 47 is introduced from the in-intermediate partition plate oil supply passage 60 into the second compression chamber 34B of the second compression mechanism 30B through the oil supply passage 36 by pressure in the in-shaft oil supply passage 46, i.e., by a pressure difference between case internal pressure in the airtight container 10 and suction pressure in the suction passage 35B of the second compression mechanism 30B.
  • Fig. 3(a) is a plan view of essential portions of a high-stage side compression mechanism of the internal medium pressure type two-stage compression compressor of the embodiment.
  • Fig. 3(b) is an enlarged plan view of essential portion of Fig. 3(a) .
  • a pressure communication groove 91 is formed in a vane-side wall surface 35B1 located on the side of a vane 33 of the suction passage 35B.
  • the pressure communication groove 91 is formed from an arc surface centering on a phantom center axis X which is parallel to a center axis of the shaft 40.
  • the pressure communication groove 91 is formed from one of end surfaces to the other end surface of the second cylinder 31B.
  • a curved surface having the same curvature as the arc surface of the pressure communication groove 91 centering on the phantom center axis X is formed on an anti-vane-side wall surface 35B2 which is opposed to the vane-side wall surface 35B1. According to this, it is possible to form the pressure communication groove 91 and an excluded volume adjusting space 92 at the same time.
  • the pressure communication groove 91 by forming the pressure communication groove 91 from the arc surface centering on the phantom center axis X which is parallel to the center axis of the shaft 40, it is possible to suppress surface pressure of the vane 33 and the vane groove, and form the pressure communication groove 91.
  • the pressure communication groove 91 by forming the pressure communication groove 91 from the one end surface to the other end surface of the second cylinder 31B, the pressure communication groove 91 can easily be formed by rotary cutting processing.
  • the excluded volume ratio of the high pressure compression excluded volume of the second compression mechanism 30B to the low pressure compression excluded volume of the first compression mechanism 30A is set to 50% to 110%. According to this, a reduction effect of oil discharge amount from the airtight container 10 can be expected.
  • carbon dioxide can be used as the refrigerant.
  • internal pressure of the airtight container 10 is set to medium pressure. Therefore, it is possible to thin a thickness of the airtight container 10, the airtight container 10 can be reduced in size and weight, and a pressure difference per one stage is reduced. Hence, volumetric efficiency is enhanced.
  • the present invention has been described based on the internal medium pressure type two-stage compression compressor, the invention can also be applied to a compression chamber having three stages or more.

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

Claims (7)

  1. Zweistufig verdichtender Kompressor vom Typ interner mittlerer Druck umfassend einen Motor (20) und einen Verdichtungsmechanismus (30) in einem luftdichten Behälter (10), bei dem
    der Motor (20) und der Verdichtungsmechanismus (30) durch eine Welle (40) miteinander verbunden sind,
    der Verdichtungsmechanismus (30) einen Zylinder (31A, 31B), einen in dem Zylinder (31A, 31B) angeordneten Kolben (32A, 32B) und einen Flügel (33) zur Unterteilung eines Innenraums des Zylinders (31A, 31B) beinhaltet,
    der Verdichtungsmechanismus (30) einen ersten Verdichtungsmechanismus (30A), der eine erste Stufe einer niederstufigen Verdichtung ausführt, und einen zweiten Verdichtungsmechanismus (30B), der eine zweite Stufe einer hochstufigen Verdichtung ausführt, beinhaltet,
    ein Ölzufuhrkanal (36) in einem Ansaugkanal (35B) des zweiten Verdichtungsmechanismus (30B) ausgebildet ist,
    Kältemittelgas, das durch den ersten Verdichtungsmechanismus (30A) komprimiert wird, in den luftdichten Behälter (10) abgegeben wird, das Kältemittelgas durch den zweiten Verdichtungsmechanismus (30B) verdichtet wird und außerhalb des luftdichten Behälters (10) abgegeben wird, und
    Öl einer zweiten Verdichtungskammer (34B) des zweiten Verdichtungsmechanismus (30B) aus dem Ölzufuhrkanal (36) durch eine Druckdifferenz zwischen dem Gehäuseinnendruck in dem luftdichten Behälter (10) und dem Ansaugdruck in dem Ansaugkanal (35B) des zweiten Verdichtungsmechanismus (30B) zugeführt wird,
    dadurch gekennzeichnet, dass, wenn sich der Kolben (32B) von einem oberen Totpunkt zu einer Position des Ansaugkanals (35B) dreht, kein geschlossener Raum zwischen dem Flügel (33), dem Zylinder (31B) und dem Kolben (32B) gebildet wird.
  2. Zweistufig verdichtender Kompressor vom Typ interner mittlerer Druck nach Anspruch 1, wobei
    eine Druckverbindungsnut (91) in einer flügelseitigen Wandfläche ausgebildet ist, die sich auf einer Seite des Flügels (33) des Ansaugkanals (35B) befindet.
  3. Zweistufig verdichtender Kompressor vom Typ interner mittlerer Druck nach Anspruch 2, wobei
    die Druckverbindungsnut (91) von einer Bogenfläche gebildet ist, die auf einer Phantom-Mittelachse zentriert ist, die parallel zu einer Mittelachse der Welle (40) ist.
  4. Zweistufig verdichtender Kompressor vom Typ interner mittlerer Druck nach Anspruch 3, wobei
    die Bogenfläche von einer der Endflächen zu einer anderen Endfläche des Zylinders (31B) gebildet wird.
  5. Zweistufig verdichtender Kompressor vom Typ interner mittlerer Druck nach Anspruch 3 oder 4, wobei
    eine gekrümmte Fläche mit derselben Krümmung wie die Bogenfläche, die auf der Phantom-Mittelachse zentriert ist, auf einer Anti-Flügel-Seitenwandfläche ausgebildet ist, die der Flügel-Seitenwandfläche gegenüberliegt.
  6. Zweistufig verdichtender Kompressor vom Typ interner mittlerer Druck nach einem der Ansprüche 1 bis 5, wobei
    ein unteres Ende der Welle (40) einen Ölabnehmer enthält,
    in der Welle (40) ein welleninterner Ölzuführungskanal (46) ausgebildet ist, durch den das von dem Ölabnehmer hochgepumpte Schmieröl fließt,
    zwischen dem ersten Verdichtungsmechanismus (30A) und dem zweiten Verdichtungsmechanismus (30B) eine Zwischentrennplatte (52) vorgesehen ist, und
    in der Zwischentrennplatte (52) ein Zwischentrennplatten-Ölzuführungskanal (60) ausgebildet ist, der das Schmieröl des welleninternen Ölzuführungskanals (46) in den Ölzuführungskanal (36) einleitet.
  7. Zweistufig verdichtender Kompressor vom Typ interner mittlerer Druck nach einem der Ansprüche 1 bis 6, wobei
    Kohlendioxid als Kältemittel verwendet wird, das durch den Verdichtungsmechanismus (30) verdichtet wird.
EP18790603.7A 2017-04-28 2018-04-24 Zweistufig verdichtender kompressor, vom typ interner mittlerer druck Active EP3617514B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017089843A JP2018188986A (ja) 2017-04-28 2017-04-28 内部中圧型２段圧縮コンプレッサ
PCT/JP2018/016541 WO2018199061A1 (ja) 2017-04-28 2018-04-24 内部中圧型２段圧縮コンプレッサ

Publications (3)

Publication Number Publication Date
EP3617514A4 EP3617514A4 (de) 2020-03-04
EP3617514A1 EP3617514A1 (de) 2020-03-04
EP3617514B1 true EP3617514B1 (de) 2023-02-22

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EP18790603.7A Active EP3617514B1 (de) 2017-04-28 2018-04-24 Zweistufig verdichtender kompressor, vom typ interner mittlerer druck

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EP (1) EP3617514B1 (de)
JP (1) JP2018188986A (de)
CN (1) CN110573741A (de)
WO (1) WO2018199061A1 (de)

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* Cited by examiner, † Cited by third party
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JP7378044B2 (ja) * 2019-11-27 2023-11-13 パナソニックＩｐマネジメント株式会社 内部中圧型多段圧縮コンプレッサ
CN112983820A (zh) * 2021-05-19 2021-06-18 广东美芝制冷设备有限公司 压缩机、制冷系统和制冷设备
JP2023005307A (ja) * 2021-06-28 2023-01-18 パナソニックＩｐマネジメント株式会社 圧縮機

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JPS6238575A (ja) * 1985-08-13 1987-02-19 Seiko Epson Corp フレキシブルデイスクドライブ
JPS63146185U (de) * 1987-03-17 1988-09-27
JP3963740B2 (ja) * 2002-03-04 2007-08-22 三洋電機株式会社 ロータリコンプレッサ
JP4136747B2 (ja) 2003-03-25 2008-08-20 三洋電機株式会社 ロータリコンプレッサ
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JP5870246B2 (ja) * 2011-05-10 2016-02-24 パナソニックＩｐマネジメント株式会社 ロータリ圧縮機
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JP2013185496A (ja) * 2012-03-08 2013-09-19 Panasonic Corp ロータリー圧縮機

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EP3617514A4 (de) 2020-03-04
WO2018199061A1 (ja) 2018-11-01
EP3617514A1 (de) 2020-03-04
CN110573741A (zh) 2019-12-13

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