EP3369932B1 - Rotary compressor - Google Patents

Rotary compressor Download PDF

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Publication number
EP3369932B1
EP3369932B1 EP16859259.0A EP16859259A EP3369932B1 EP 3369932 B1 EP3369932 B1 EP 3369932B1 EP 16859259 A EP16859259 A EP 16859259A EP 3369932 B1 EP3369932 B1 EP 3369932B1
Authority
EP
European Patent Office
Prior art keywords
muffler
discharge openings
discharge
rotary compressor
interval
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16859259.0A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3369932A1 (en
EP3369932A4 (en
Inventor
Shunsuke Yakushiji
Makoto Ogawa
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems Ltd
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Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP3369932A1 publication Critical patent/EP3369932A1/en
Publication of EP3369932A4 publication Critical patent/EP3369932A4/en
Application granted granted Critical
Publication of EP3369932B1 publication Critical patent/EP3369932B1/en
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Anticipated expiration legal-status Critical

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

Definitions

  • the present invention is related to a rotary compressor used in refrigerating equipment.
  • a cylinder 2 having a cylindrical inner wall surface and a piston rotor 3 provided eccentrically with respect to a center of the cylinder 2 are provided in the interior of a sealed container 1.
  • the piston rotor 3 is provided on a main shaft 4, which is provided along a central axis of the cylinder 2.
  • the main shaft 4 is provided so as to rotate freely about the central axis via an upper bearing 5A and a lower bearing 5B that are fixed to the cylinder 2.
  • a rotor 6A of a motor 6 is fixed to the main shaft 4.
  • a stator 6B, which is fixed to an internal peripheral surface of the sealed container 1, is disposed on an outer peripheral side of the rotor 6A.
  • the rotary compressor sucks refrigerant into a compression chamber formed between the cylinder 2 and the piston rotor 3, and compresses the refrigerant by decreasing a volume of the compression chamber as a result of the rotation of the piston rotor 3.
  • the compressed refrigerant is discharged into an upper muffler 7A and a lower muffler 7B from a discharge opening, which is not illustrated, and then reaches the sealed container 1.
  • the rotary compressor sucks up and compresses the refrigerant after performing gas-liquid separation on the refrigerant using an accumulator 8.
  • Patent Document 1 discloses an upper cover (corresponding to a muffler) having a two-layer structure of a first internal cover and a second external cover and a lower cover which is a third cover having a single-layer structure.
  • a refrigerant discharged from the third cover flows into an interior of the second upper cover (exterior of the first cover).
  • the first cover and the third cover share the use of the second cover.
  • Pulsation generated by a compression motion of a rotary compression mechanism formed of a cylinder and a piston rotor excites an acoustic eigenvalue and a structure eigenvalue while a refrigerant passes through an output flow passage. This induces vibration of the rotary compressor, thereby resulting in noise.
  • the pulsation due to the compression motion can be reduced by providing a two-layer structured muffler as disclosed in Patent Document 1.
  • pulsation based on the acoustic eigenvalue of the muffler itself cannot be reduced, and the pulsation thus leaks from the muffler.
  • a rotary compressor includes: a sealed container, a rotary compression mechanism configured to compress and discharge a refrigerant that is supplied; an upper bearing and a lower bearing provided sandwiching the rotary compression mechanism; a main shaft rotatably supported by both the upper bearing and the lower bearing and extending through the rotary compression mechanism; an electric motor configured to rotationally drives the main shaft about a central axis of the main shaft; and a muffler into which the refrigerant discharged from the rotary compressor mechanism flows via a discharge port provided in the upper bearing, the rotary compression mechanism, the upper bearing and the lower bearing, the main shaft, the electrical motor, and the muffler being housed in the sealed container.
  • the muffler of the rotary compressor includes a first muffler provided on an inner side, and a second muffler provided on an outer side of the first muffler and covering the first muffler.
  • An acoustic eigenvalue of a frequency F that is pre-specified is excited in the first muffler.
  • the second muffler absorbs a sound wave of the frequency F transmitted through the first muffler.
  • the interval between the plurality of first discharge openings can be an interval on a side that does not include the discharge port.
  • the plurality of first discharge openings can be disposed on the same circumference.
  • the plurality of first discharge openings and the plurality of second discharge openings can be disposed on the same circumference.
  • at least one of the plurality of second discharge openings can be adjacent to the plurality of first discharge openings on both sides of the at least one of the plurality of second discharge openings in a circumferential direction.
  • the plurality of second discharge openings can be disposed on the same circumference. Furthermore, the single first discharge opening and the plurality of second discharge openings can be disposed on the same circumference.
  • a position/positions of the single first discharge opening or the plurality of first discharge openings and positions of the plurality of second discharge openings are preferably displaced from one another without overlapping in a plan view of the first muffler and the second muffler.
  • the upper bearing 29A and the lower bearing 29B are disposed so that the base portion 291A and the base portion 291B face each other.
  • the upper bearing 29A supports the main shaft 23 between the cylinder 20A and the electric motor 36.
  • 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. 3A ) that communicates with the discharge opening (not illustrated in the drawings) formed in the cylinder 20A, and the refrigerant that has passed through the cylinder 20A passes through the discharge port 294A and is discharged to the interior of the upper muffler 50 that will be described below.
  • the lower bearing 29B is provided with a discharge port (not illustrated in the drawings) that communicates with the discharge opening (not illustrated in the drawings) formed in the cylinder 20B, and the refrigerant that has passed through the cylinder 20B passes through the discharge port and is discharged to the interior of a lower muffler 60 that will be described below.
  • Openings 12A and 12B are formed in the sides of the sealed container 11, in positions facing outer peripheral surfaces of the cylinders 20A and 20B.
  • Intake ports 30A and 30B that communicate as far as predetermined positions of the cylinder internal wall surfaces 20S are formed in the cylinders 20A and 20B, in positions facing the openings 12A and 12B.
  • an accumulator 14 which performs gas-liquid separation of the refrigerant before the refrigerant is supplied to the compressor 10, is fixed to the sealed container 11 via a stay 15.
  • the compressor 10 takes up the refrigerant into the accumulator 14 from an intake port 14a of the accumulator 14, performs gas-liquid separation on the refrigerant inside the accumulator 14, and supplies the resulting gas phase from the intake pipes 16A and 16B to the compression chambers R1 and R2, which are internal spaces of the cylinders 20A and 20B, via the intake ports 30A and 30B of the cylinders 20A and 20B.
  • the volume of the compression chambers R1 and R2 is gradually decreased by the eccentric rotation of the piston rotors 21A and 21B, and the refrigerant is compressed.
  • the compressed refrigerant passes through the upper bearing 29A and the upper muffler 50 near the cylinder 20A and passes through the lower bearing 29B and the lower muffler 60 near the cylinder 20B, and is discharged into the interior of the sealed container 11 and the outside of the upper muffler 50 and the lower muffler 60.
  • the refrigerant After passing through the electric motor 36, the refrigerant is exhausted to a pipe that forms a refrigerant cycle, via a discharge port 42 provided in an upper portion.
  • the first muffler 50A is provided with a flange 51A and a cup 52A that stands up from the flange 51A.
  • the flange 51 and the cup 52 are integrally formed by sheet metal working of a flat metal plate such as an aluminum alloy plate, for example.
  • the flange 51A is a portion that is used to fix the upper muffler 50 to the upper bearing 29A, and is a flat member having a circular external shape in a plan view. While the flange 51 abuts a top surface of the upper bearing 29A without any gap therebetween, the flange 51A is fixed to the upper bearing 29A in a plurality of locations, which are five locations in the present embodiment, by the plurality of bolts B that penetrate through the flange 51A. Note that portions to which the bolts B of the flange 51A are attached are provided in indentations that are formed by a side wall 54A of the cup 52A being indented toward a center of the cup 52A in the radial direction.
  • the cup 52A is provided with the hollow cylindrical side wall 54A and a top plate 55A that covers an opening at an upper end of the side wall 54A.
  • the top plate 55A has a ring shape with an outer periphery and an inner periphery, and the outer periphery side is connected to the side wall 54A while the inner periphery side abuts the sleeve 292A of the upper bearing 29A.
  • the second muffler 50B has the same basic configuration as that of the first muffler 50A, so that the same components as those of the first muffler 50A are denoted by the references in which A is changed to B in FIGS. 1 to 3B , and their description will be omitted.
  • the first muffler 50A has two first discharge openings 56A1 and 56A2 formed so as to penetrate the back and front of the top plate 55A, and the second muffler 50B has three second discharge openings 56B1, 56B2, and 56B3 formed so as to penetrate the back and front of the top plate 55B.
  • the compressed refrigerant passes through in the order of the discharge ports 294A and 294B of the upper bearing 29A, the internal space of the first muffler 50A, the first discharge openings 56A1 and 56A2 of the first muffler 50A, the space between the second muffler 50B and the first muffler 50A, and the second discharge openings 56B1, 56B2, and 56B3 of the second muffler 50B.
  • the first discharge openings 56A1 and 56A2 and the second discharge openings 56B1, 56B2, and 56B3 are formed so as to be displaced from one another without overlapping in the plan view of the first muffler 50A and the second muffler 50B.
  • the compressed refrigerant is prevented from passing through the second discharge opening 56B1 directly from the first discharge opening 56A1.
  • Positions of the first discharge openings 56A1 and 56A2 of the first muffler 50A and the second discharge openings 56B1, 56B2, and 56B3 of the second muffler 50B are specified as follows.
  • the interval L1 herein is an interval on a side that does not include the discharge ports 294A and 294B.
  • the interval L1 is the interval on the side that does not include the discharge ports 294A and 294B, but an interval on a side that includes the discharge ports 294A and 294B can be the interval L1 depending on an interval between the discharge port 294A and the discharge port 294B.
  • the second muffler 50B absorbs a sound wave of the frequency F that is transmitted through the first muffler 50A, and suppresses transmission of the pulsation to the outside of the second muffler 50B.
  • the positions of the second discharge openings 56B1, 56B2, and 56B3 of the second muffler 50B are set such that an interval L2 between adjacent discharge openings including the first discharge openings 56A1 and 56A2 is 1/2 the interval L1 between the first discharge openings 56A1 and 56A2.
  • FIG. 4B schematically illustrates what has been described so far. It is the most preferable manner that the interval L2 herein is 1/2 L1, but the effects of the present invention can be still obtained even if the interval L2 is slightly deviated from 1/2 L2. In other words, the interval L2 can be determined with 1/2L1 as a base in the present invention.
  • the upper muffler 50 has the two-layer structure of the first muffler 50A and the second muffler 50B, and the frequency F at which a sound wants to be silenced in the first muffler 50A can be specified. Thus, pulsation of a target frequency can be reliably reduced.
  • pulsation by a refrigerant immediately after being discharged from a compression chamber has a large frequency component determined by dimensions of the compression chamber. If the pulsation of this frequency can be reduced in the present embodiment, a problem of noise due to the pulsation can be mostly solved. Particularly in the present embodiment, only the interval L1 between the first discharge openings 56A1 and 56A2 and the intervals L2 between the second discharge openings 56B1, 56B2, and 56B3 need to be adjusted, so that the pulsation can be reduced at low cost.
  • the embodiment described above illustrates the example of providing the two first discharge openings 56A1 and 56A2 of the first muffler 50A, but the present invention is also applicable to a case where a single first discharge opening 56A1 is provided in the first muffler 50A as illustrated in FIG. 5A .
  • intervals between the second discharge openings 56B1, 56B2, and 56B3 are determined as illustrated in FIG. 5B with an interval L1 or an interval L3 between the discharge port 294A and the first discharge opening 56A1 illustrated in FIG. 5A as a base.
  • the discharge port 294A is not taken into consideration for specifying the interval L1 (interval L2) in the embodiment described above because the interval between the discharge port 294A and the first discharge opening 56A1 is extremely small, the corresponding frequency is high, and it is determined that the discharge port 294A does not need to be targeted for noise reduction.
  • the present invention is also applicable to a case where three or more first discharge openings 56A1, 56A2, and 56A3 are provided in the first muffler 50A.
  • the second discharge openings 56B1, 56B2, and 56B3 are provided in the second muffler 50B.
  • the two-cylinder type rotary compressor is the example of the upper muffler 50, but the present invention is also applicable to a muffler of a one-cylinder type rotary compressor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP16859259.0A 2015-10-27 2016-10-06 Rotary compressor Active EP3369932B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015210285A JP6625864B2 (ja) 2015-10-27 2015-10-27 ロータリ式圧縮機
PCT/JP2016/004503 WO2017073019A1 (ja) 2015-10-27 2016-10-06 ロータリ式圧縮機

Publications (3)

Publication Number Publication Date
EP3369932A1 EP3369932A1 (en) 2018-09-05
EP3369932A4 EP3369932A4 (en) 2018-10-10
EP3369932B1 true EP3369932B1 (en) 2021-03-31

Family

ID=58631384

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16859259.0A Active EP3369932B1 (en) 2015-10-27 2016-10-06 Rotary compressor

Country Status (4)

Country Link
EP (1) EP3369932B1 (zh)
JP (1) JP6625864B2 (zh)
CN (1) CN107614881B (zh)
WO (1) WO2017073019A1 (zh)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3885589B1 (en) 2020-03-25 2022-05-04 Bollhoff Otalu S.A. Blind rivet insert, a component with an installed blind rivet insert and method for installing such a blind rivet insert in a component opening
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

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6039517Y2 (ja) * 1979-07-12 1985-11-26 松下電器産業株式会社 密閉型圧縮機の消音装置
JPH05133377A (ja) * 1991-11-12 1993-05-28 Sanyo Electric Co Ltd 密閉型圧縮機
KR20030051084A (ko) * 2001-12-20 2003-06-25 주식회사 엘지이아이 회전식 압축기의 소음 저감장치
WO2007074637A1 (ja) * 2005-12-28 2007-07-05 Daikin Industries, Ltd. 圧縮機
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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP3369932A1 (en) 2018-09-05
EP3369932A4 (en) 2018-10-10
JP6625864B2 (ja) 2019-12-25
JP2017082632A (ja) 2017-05-18
CN107614881A (zh) 2018-01-19
WO2017073019A1 (ja) 2017-05-04
CN107614881B (zh) 2019-06-21

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