WO2017073019A1 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

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Publication number
WO2017073019A1
WO2017073019A1 PCT/JP2016/004503 JP2016004503W WO2017073019A1 WO 2017073019 A1 WO2017073019 A1 WO 2017073019A1 JP 2016004503 W JP2016004503 W JP 2016004503W WO 2017073019 A1 WO2017073019 A1 WO 2017073019A1
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WO
WIPO (PCT)
Prior art keywords
muffler
discharge ports
rotary compressor
discharge port
interval
Prior art date
Application number
PCT/JP2016/004503
Other languages
English (en)
Japanese (ja)
Inventor
俊輔 薬師寺
小川　真
Original Assignee
三菱重工業株式会社
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Priority to CN201680025135.0A priority Critical patent/CN107614881B/zh
Priority to EP16859259.0A priority patent/EP3369932B1/fr
Publication of WO2017073019A1 publication Critical patent/WO2017073019A1/fr

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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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/061—Silencers using overlapping frequencies, e.g. Helmholtz resonators

Definitions

  • the present invention relates to a rotary compressor used in a refrigeration apparatus.
  • the rotary compressor used in the refrigeration apparatus includes a cylinder 2 having a cylindrical inner wall surface and a piston provided eccentrically with respect to the center of the cylinder 2. And a rotor 3.
  • the piston rotor 3 is provided on a main shaft 4 provided along the central axis of the cylinder 2.
  • the main shaft 4 is provided so as to be rotatable around its central axis via an upper bearing 5A and a lower bearing 5B fixed to the cylinder 2.
  • a rotor 6 ⁇ / b> A of a motor 6 is fixed to the main shaft 4.
  • a stator 6B fixed to the inner peripheral surface of the hermetic container 1 is disposed.
  • the rotary compressor in FIG. 7 is a two-cylinder type compressor that includes two pairs of a cylinder 2 and a piston rotor 3 at the top and bottom.
  • the rotary compressor sucks the refrigerant into a compression chamber formed between the cylinder 2 and the piston rotor 3, and compresses the refrigerant by reducing the volume of the compression chamber by the rotation of the piston rotor 3.
  • the compressed refrigerant is discharged from a discharge port (not shown) to the upper muffler 7A and the lower muffler 7B, and then reaches the sealed container 1.
  • the rotary compressor separates the refrigerant from gas and liquid by the accumulator 8 and then sucks and compresses the refrigerant.
  • the upper cover (corresponding to a muffler) has a two-layer structure of an inner first cover and an outer second cover, and the lower cover has a single-layer structure of a third cover.
  • the refrigerant discharged from the third cover is caused to flow into the upper second cover (outside the first cover).
  • the first cover and the third cover share the second cover, and in addition to the two-stage silencing by the flow path connecting the first cover to the second cover, the third cover is connected to the second cover. Two stages of noise reduction are realized by the flow path.
  • an object of the present invention is to provide a rotary compressor that can reduce pulsation based on the acoustic eigenvalue of the muffler itself by using a muffler having a two-layer structure.
  • a rotary compressor according to the present invention is rotatable in each of a rotary compression mechanism that compresses and discharges a supplied refrigerant, an upper bearing and a lower bearing provided across the rotary compression mechanism, and an upper bearing and a lower bearing.
  • a muffler to be stored in a sealed container.
  • the muffler of the rotary compressor of the present invention has a first muffler provided inside, and a second muffler that is outside the first muffler and covers the first muffler, and the first muffler is specified in advance.
  • the acoustic characteristic value of the frequency F is excited, and the second muffler absorbs the sound wave of the frequency F that passes through the first muffler.
  • the first muffler includes a plurality of first discharge ports that discharge the refrigerant that has flowed into the second muffler, and the second muffler passes through the first discharge port to the inside.
  • a plurality of second discharge ports are provided for discharging the flowed refrigerant into the sealed container, and the interval between the plurality of second discharge ports is based on 1 ⁇ 2 of the interval between the plurality of first discharge ports. Can be determined.
  • the interval between the first discharge ports can be set to the interval passing the side where the discharge port is not provided.
  • interval of a 1st discharge outlet can be specified so that the frequency of an acoustic eigenvalue may be excited.
  • the first muffler may have two first discharge ports, and the second muffler may have three or more second discharge ports.
  • the plurality of first discharge ports can be arranged on the same circumference.
  • a plurality of second discharge ports can be arranged on the same circumference.
  • the plurality of first discharge ports and the plurality of second discharge ports can be arranged on the same circumference.
  • at least one second discharge port can be adjacent to the first discharge port on both sides in the circumferential direction.
  • the first discharge port and the plurality of second discharge ports can be arranged radially inward from the discharge port.
  • the first muffler includes a single first discharge port that discharges the flowing refrigerant into the second muffler, and the second muffler passes through the first discharge port to the inside.
  • a plurality of second discharge ports are provided to discharge the refrigerant flowing into the closed container, and the interval between the plurality of second discharge ports is 1 ⁇ 2 of the interval between the first discharge port and the discharge port. It can be determined by reference.
  • a plurality of second discharge ports can be arranged on the same circumference. Moreover, a single first discharge port and a plurality of second discharge ports can be arranged on the same circumference.
  • the position where the single or plural first discharge ports are provided overlaps with the position where the plural second discharge ports are provided in plan view of the first muffler and the second muffler. It is preferable that it has shifted
  • the rotary compressor includes a two-layered muffler having a first muffler provided inside, and a second muffler that is outside the first muffler and covers the first muffler, It is assumed that one muffler is excited with an acoustic eigenvalue of a frequency F specified in advance, and that the second muffler absorbs a sound wave having a frequency F that passes through the first muffler, so that the muffler itself has an acoustic eigenvalue.
  • the pulsation based can be reduced.
  • FIG. 1 It is a longitudinal section showing a schematic structure of a rotary type compressor concerning an embodiment of the present invention. It is the elements on larger scale of FIG.
  • the muffler of the rotary compressor of FIG. 1 is shown, (a) is a top view of a 1st muffler, (b) is a top view of a 2nd muffler. (A) is a top view which shows typically the muffler by which arrangement
  • the compressor 10 includes a rotary compression mechanism, and an upper muffler 50 to be described later has a two-layer structure, and the arrangement of refrigerant discharge ports in each layer is specified, whereby the upper muffler 50 is identified. Suppresses pulsation based on its own acoustic eigenvalue.
  • the configuration of the compressor 10 will be described, and then the operation and effect of the compressor 10 will be described.
  • the compressor 10 is a so-called two-cylinder rotary compressor in which disk-shaped cylinders 20 ⁇ / b> A and 20 ⁇ / b> B provided in two upper and lower stages are accommodated in a cylindrical sealed container 11. is there.
  • a cylindrical cylinder inner wall surface 20S is formed in each of the cylinders 20A and 20B.
  • Cylindrical piston rotors 21A and 21B each having an outer diameter smaller than the inner diameter of the cylinder inner wall surface 20S are arranged inside the cylinders 20A and 20B.
  • the piston rotors 21A and 21B are inserted and fixed to the eccentric shaft portions 40A and 40B of the main shaft 23 along the central axis of the sealed container 11, respectively.
  • a disc-shaped partition plate 24 is provided between the upper cylinder 20A and the lower cylinder 20B. The partition plate 24 partitions the space of the upper cylinder 20A and the space of the lower cylinder 20B into the compression chamber R1 and the compression chamber R2 without communicating with each other.
  • the upper and lower cylinders 20A and 20B are provided with blades (not shown) for dividing the compression chambers R1 and R2 into two, respectively.
  • the blade is held by an insertion groove formed extending in the radial direction of the cylinders 20A and 20B so as to be able to advance and retreat in a direction toward and away from the piston rotors 21A and 21B.
  • the cylinders 20A and 20B each have a discharge port (not shown) for discharging the refrigerant at a predetermined position, and the discharge port is provided with a reed valve (not shown). When the pressure of the compressed refrigerant reaches a predetermined value, the refrigerant is discharged to the outside of the cylinders 20A and 20B by pushing the reed valve open.
  • the main shaft 23 is rotatably supported around its central axis by an upper bearing 29A fixed to the cylinder 20A and a lower bearing 29B fixed to the cylinder 20B.
  • the upper bearing 29A and the lower bearing 29B are provided with a rotary compression mechanism interposed therebetween.
  • the main shaft 23 includes eccentric shaft portions 40A and 40B that are offset in a direction orthogonal to the central axis of the main shaft 23, that is, are shifted in position.
  • the eccentric shaft portions 40A and 40B have outer diameters slightly smaller than the inner diameters of the piston rotors 21A and 21B.
  • the main shaft 23 protrudes and extends upward from the upper bearing 29A, and a rotor 37 of an electric motor 36 for rotating the main shaft 23 is integrally provided in the protruding portion.
  • a stator 38 facing the outer peripheral portion of the rotor 37 is fixed to the inner peripheral surface of the sealed container 11.
  • the upper bearing 29A includes a base 291A and a sleeve 292A that rises vertically from the base 291A.
  • the base portion 291A and the sleeve 292A are formed so that their axial centers coincide with each other, and a receiving surface 293A for supporting the main shaft 23 is formed around the axial center.
  • the outer peripheral surface of the base portion 291A is fixed to the inner peripheral surface of the sealed container 11 at a plurality of fixing points. This fixing is performed by, for example, welding or fastening with a bolt.
  • the lower bearing 29B includes a base 291B and a sleeve 292B that rises vertically from the base 291B.
  • the base 291 ⁇ / b> B and the sleeve 292 ⁇ / b> B are formed so that their axes coincide with each other, and a receiving surface 293 ⁇ / b> B for supporting the main shaft 23 is formed around the axis.
  • the upper bearing 29A and the lower bearing 29B are disposed so that the base 291A and the base 291B face each other.
  • the upper bearing 29A supports the main shaft 23 between the cylinder 20A and the electric motor 36, and the lower bearing 29B supports the main shaft 23 at a portion protruding downward from the cylinder 20B.
  • the upper bearing 29A is provided with a discharge port 294A (see FIG.
  • the lower bearing 29B includes a discharge port (not shown) communicating with a discharge port (not shown) formed in the cylinder 20B, and the refrigerant passing through the cylinder 20B passes through the discharge port and passes through the lower muffler 60. It is discharged into the inside of.
  • Compressor 10 has upper muffler 50 mounted on upper bearing 29A and lower muffler 60 mounted on lower bearing 29B.
  • the refrigerant that has passed through the upper bearing 29A and the lower bearing 29B flows into the upper muffler 50 and the lower muffler 60, respectively, the pulsating component is removed.
  • the refrigerant from which the pulsating component has been removed flows toward the upper side of the sealed container 11 through the first discharge port 56A formed in the upper muffler 50 and the second discharge port 56B formed in the lower muffler 60. Details of the upper muffler 50 will be described later.
  • Openings 12A and 12B are formed on the side of the sealed container 11 at positions facing the outer peripheral surfaces of the cylinders 20A and 20B.
  • suction ports 30A and 30B are formed at positions facing the openings 12A and 12B to communicate with a predetermined position on the cylinder inner wall surface 20S.
  • an accumulator 14 for gas-liquid separation of the refrigerant Prior to supplying the compressor 10 to the compressor 10, an accumulator 14 for gas-liquid separation of the refrigerant is fixed to the sealed container 11 via a stay 15.
  • the accumulator 14 is provided with suction pipes 16A and 16B for letting the compressor 10 suck the refrigerant in the accumulator 14.
  • the distal ends of the suction pipes 16A and 16B pass through the openings 12A and 12B and are connected to the suction ports 30A and 30B.
  • the compressor 10 takes in the refrigerant into the accumulator 14 from the suction port 14a of the accumulator 14, separates the refrigerant in the accumulator 14, and the gas phase is sucked into the cylinders 20A and 20B from the suction pipes 16A and 16B.
  • the gas is supplied to compression chambers R1 and R2 that are internal spaces of the cylinders 20A and 20B via the ports 30A and 30B. Then, by eccentrically rolling the piston rotors 21A and 21B, the volumes of the compression chambers R1 and R2 are gradually reduced, and the refrigerant is compressed.
  • the compressed refrigerant passes through the upper bearing 29A and the upper muffler 50 on the cylinder 20A side, and passes through the lower bearing 29B and the lower muffler 60 on the cylinder 20B side. It is discharged to the outside of the upper muffler 50 and the lower muffler 60 inside. After passing through the electric motor 36, the refrigerant is discharged to the piping constituting the refrigeration cycle via the discharge port 42 provided at the top.
  • the upper muffler 50 that is a feature of the present embodiment will be described.
  • the upper muffler 50 is a two-layer structure including a first muffler 50A provided inside and a second muffler 50B outside the first muffler 50A and covering the first muffler 50A.
  • Each has a structure and is fixed to the upper bearing 29A by a plurality of bolts B.
  • the first muffler 50A includes a flange 51A and a cup 52A that rises from the flange 51A.
  • a flange 51A and a cup 52A are integrally formed by subjecting a flat metal plate such as an aluminum alloy plate to sheet metal processing.
  • the flange 51A is a portion provided to fix the upper muffler 50 to the upper bearing 29A, and is a flat member whose outer shape is circular in plan view.
  • the flange 51A is abutted against the upper surface of the upper bearing 29A without any gap, and is fixed to the upper bearing 29A at a plurality of locations, in this embodiment, at five locations by a plurality of bolts B penetrating the flange 51A.
  • bolt B of the flange 51A is fixed is provided in the aperture_diaphragm
  • the cup 52A includes a hollow cylindrical side wall 54A and a top plate 55A that covers the opening at the upper end of the side wall 54A.
  • the top plate 55A has a ring shape having an outer periphery and an inner periphery, the outer periphery is connected to the side wall 54A, and the inner periphery is abutted against the sleeve 292A of the upper bearing 29A.
  • the same elements as those of the first muffler 50A are denoted by the reference numerals in which A is changed to B in FIGS. The description is omitted.
  • the upper muffler 50 passes through a refrigerant path through which compressed refrigerant discharged from discharge ports 294A and 294B (FIG. 3A) provided in the upper bearing 29A passes in order of the first muffler 50A and the second muffler 50B.
  • the air is discharged inside the sealed container 11 and outside the upper muffler 50 and the lower muffler 60.
  • the discharge port 294B is for the compressed refrigerant once discharged to the lower muffler 60 to be discharged to the first muffler 50A through the lower bearing 29B and further through the upper bearing 29A. In order to form this refrigerant path, as shown in FIG.
  • the first muffler 50A has two first discharge ports 56A1 and 56A2 formed through the front and back of the top plate 55A.
  • 50B has three 2nd discharge outlets 56B1, 56B2, and 56B3 formed through the front and back of the top plate 55B. That is, the compressed refrigerant is the discharge ports 294A and 294B of the upper bearing 29A, the internal space of the first muffler 50A, the first discharge ports 56A1 and 56A2 of the first muffler 50A, and the space between the second muffler 50B and the first muffler 50A. And the second outlets 56B1, 56B2, and 56B3 of the second muffler 50B pass in this order.
  • the first discharge ports 56A1 and 56A2 and the second discharge ports 56B1, 56B2, and 56B3 are formed so as not to overlap with each other in plan view of the first muffler 50A and the second muffler 50B.
  • the compressed refrigerant is prevented from passing directly through the second discharge port 56B1 from the discharge port 56A1.
  • the positions of the first discharge ports 56A1, 56A2 of the first muffler 50A and the second discharge ports 56B1, 56B2, 56B3 of the second muffler 50B are specified as follows.
  • the positions of the first outlets 56A1 and 56A2 are specified so that the acoustic eigenvalue of the frequency F to be silenced by the first muffler 50A is excited most strongly.
  • the acoustic eigenvalue is specified by the mutual interval L1 along the circumferential direction of the first discharge port 56A1 and the discharge port 56A2.
  • the first muffler 50A can be actively expanded and contracted at the frequency F to be silenced, and pulsation energy can be converted into heat energy to suppress pulsation.
  • the first discharge port 56A1 and the first discharge port 56A2 can have two mutual intervals along the circumferential direction, but the interval L1 here passes through the side where the discharge ports 294A and 294B are not provided. And In this embodiment, the interval L1 is set to pass through the side where the discharge ports 294A and 294B are not provided, but the discharge ports 294A and 294B are provided depending on the interval between the discharge port 294A and the discharge port 294B. The direction passing the side can also be set as the interval L1.
  • the second muffler 50B absorbs the sound wave having the frequency F that passes through the first muffler 50A, and suppresses the transmission of pulsation to the outside of the second muffler 50B. Therefore, the second discharge ports 56B1, 56B2, and 56B3 of the second muffler 50B are arranged such that the interval L2 between adjacent discharge ports including the first discharge ports 56A1 and 56A2 is the interval between the first discharge ports 56A1 and 56A2. It is set to be 1/2 of L1. In FIG.
  • the interval L2 between the second discharge port 56B1 and the discharge port 56B3 is 1 / 2L1
  • the interval L2 between the discharge port 56B3 and the discharge port 56A2 is 1 / 2L1
  • the second discharge port 56B2 and the first discharge port is 1 / 2L1.
  • the second muffler 50B resonates at half the wavelength of the sound wave that resonates with the first muffler 50A, and therefore can absorb the sound wave transmitted through the first muffler 50A.
  • the interval L2 here is 1 / 2L1, which is the most preferable form, but the effect of the present invention can be enjoyed even if the interval L2 is slightly shifted from 1 / 2L2. That is, according to the present invention, the interval L2 can be determined with reference to 1 / 2L1.
  • the upper muffler 50 has a two-layer structure of the first muffler 50A and the second muffler 50B, and the frequency F to be silenced by the first muffler 50A can be specified. Therefore, the pulsation of the targeted frequency can be reliably reduced.
  • the pulsation caused by the refrigerant immediately after being discharged from the compression chamber has a strong frequency component determined by the dimensions of the compression chamber, and if the pulsation of this frequency can be reduced by this embodiment, the problem of noise caused by the pulsation is reduced. It can be almost solved.
  • the configuration described in the above embodiment can be selected or changed to another configuration as appropriate.
  • the example in which the two first discharge ports 56A1 and 56A2 of the first muffler 50A are provided has been shown.
  • the first muffler 50A has a single first discharge port.
  • the present invention can also be applied when 56A1 is provided. In this case, based on the interval L1 or interval L3 between the discharge port 294A and the first discharge port 56A1 shown in FIG. 5A, as shown in FIG. 5B, the second discharge ports 56B1, 56B2, and 56B3. Determine the interval.
  • the discharge port 294A is not considered in specifying the interval L1 (interval L2), but this is because the interval between the discharge port 294A and the first discharge port 56A1 is extremely narrow, and the corresponding frequency is high. This is because it has been determined that there is no need for mute.
  • the present invention can also be applied when three or more first discharge ports 56A1, 56A2, and 56A3 are provided in the first muffler 50A.
  • the second muffler 50B is provided with second discharge ports 56B1, 56B2, and 56B3.
  • the upper muffler 50 of the two-cylinder type rotary compressor is taken as an example, but the present invention can also be applied to the muffler of the one-cylinder type rotary compressor.

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

Abstract

L'invention concerne un compresseur rotatif au moyen duquel il est possible de réduire la pulsation sur la base d'une valeur inhérente acoustique d'un silencieux structuré en deux couches. Ce compresseur rotatif 10 est caractérisé en ce que : un silencieux supérieur 50 comprend un premier silencieux 50A disposé sur le côté intérieur, et un second silencieux 50B disposé sur le côté extérieur du premier silencieux 50A et recouvrant le premier silencieux 50A ; la valeur inhérente acoustique de la fréquence prédéfinie F est excitée dans le premier silencieux 50A ; et le second silencieux 50B absorbe des ondes sonores d'une fréquence F qui traversent le premier silencieux 50A. Les espaces L2 entre des seconds orifices d'évacuation 56B1, 56B2, 56B3 du second silencieux 50B équivalent à 1/2 de l'intervalle L1 entre des premiers orifices d'évacuation 56A1 et 56A2 du premier silencieux 50A, constituant la configuration la plus efficace en vue d'obtenir les effets de la présente invention.
PCT/JP2016/004503 2015-10-27 2016-10-06 Compresseur rotatif WO2017073019A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201680025135.0A CN107614881B (zh) 2015-10-27 2016-10-06 旋转式压缩机
EP16859259.0A EP3369932B1 (fr) 2015-10-27 2016-10-06 Compresseur rotatif

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015-210285 2015-10-27
JP2015210285A JP6625864B2 (ja) 2015-10-27 2015-10-27 ロータリ式圧縮機

Publications (1)

Publication Number Publication Date
WO2017073019A1 true WO2017073019A1 (fr) 2017-05-04

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PCT/JP2016/004503 WO2017073019A1 (fr) 2015-10-27 2016-10-06 Compresseur rotatif

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EP (1) EP3369932B1 (fr)
JP (1) JP6625864B2 (fr)
CN (1) CN107614881B (fr)
WO (1) WO2017073019A1 (fr)

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Publication number Priority date Publication date Assignee Title
ES2924088T3 (es) 2020-03-25 2022-10-04 Bollhoff Otalu Sa Pieza de inserción de remache ciega, un componente con una pieza de inserción de remache ciega instalada, y método para instalar dicha pieza de inserción de remache ciega en una abertura del componente
CN113864197B (zh) * 2021-10-25 2023-03-21 珠海格力电器股份有限公司 一种泵体结构、压缩机及空调器

Citations (2)

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Publication number Priority date Publication date Assignee Title
JPS5613565U (fr) * 1979-07-12 1981-02-05
JPH05133377A (ja) * 1991-11-12 1993-05-28 Sanyo Electric Co Ltd 密閉型圧縮機

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Publication number Priority date Publication date Assignee Title
KR20030051084A (ko) * 2001-12-20 2003-06-25 주식회사 엘지이아이 회전식 압축기의 소음 저감장치
AU2006329386B2 (en) * 2005-12-28 2010-02-04 Daikin Industries, Ltd. Compressor
JP2008002366A (ja) * 2006-06-23 2008-01-10 Matsushita Electric Ind Co Ltd 多気筒圧縮機
CN203130519U (zh) * 2013-02-04 2013-08-14 安徽美芝精密制造有限公司 压缩机的消音器及具有其的压缩机
JP6161923B2 (ja) * 2013-03-12 2017-07-12 三菱重工業株式会社 ロータリー圧縮機
CN103967800B (zh) * 2014-05-19 2016-08-24 松下·万宝(广州)压缩机有限公司 阻抗复合型排气消音器及具有该消音器的压缩机

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5613565U (fr) * 1979-07-12 1981-02-05
JPH05133377A (ja) * 1991-11-12 1993-05-28 Sanyo Electric Co Ltd 密閉型圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3369932A4 *

Also Published As

Publication number Publication date
CN107614881B (zh) 2019-06-21
CN107614881A (zh) 2018-01-19
JP6625864B2 (ja) 2019-12-25
EP3369932B1 (fr) 2021-03-31
JP2017082632A (ja) 2017-05-18
EP3369932A4 (fr) 2018-10-10
EP3369932A1 (fr) 2018-09-05

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