EP3015712B1 - Rotary compressor - Google Patents

Rotary compressor Download PDF

Info

Publication number
EP3015712B1
EP3015712B1 EP14849841.3A EP14849841A EP3015712B1 EP 3015712 B1 EP3015712 B1 EP 3015712B1 EP 14849841 A EP14849841 A EP 14849841A EP 3015712 B1 EP3015712 B1 EP 3015712B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
intake
intake port
rotary compressor
intake pipe
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
EP14849841.3A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3015712A4 (en
EP3015712A1 (en
Inventor
Makoto Ogawa
Ikuo Esaki
Masanari Uno
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
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 Mitsubishi Heavy Industries Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP3015712A1 publication Critical patent/EP3015712A1/en
Publication of EP3015712A4 publication Critical patent/EP3015712A4/en
Application granted granted Critical
Publication of EP3015712B1 publication Critical patent/EP3015712B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/101—Geometry of the inlet or outlet of the inlet

Definitions

  • the present invention relates to a multi-cylinder rotary compressor provided with a plurality of cylinders.
  • a plurality of cylinder chambers are constituted by providing a plurality of cylinders in the direction of a rotating shaft, sandwiching a separator plate between the cylinders, closing one end of each cylinder using the separator plate, and closing the other end using each bearing member.
  • a rotor (piston) that rotates along an inner peripheral surface of each cylinder chamber is rotatably provided in an eccentric shaft part of the rotating shaft (crankshaft), and a compression operation is performed by the eccentric rotation of the rotor.
  • Patent Document 1 there is provided a rotary compressor in which a rotating shaft is made dividable by a center shaft part between eccentric shaft parts, and the divided rotating shafts are integrally linked with each other after a separator plate is inserted into the center shaft part.
  • JP H03 222887 discloses a two-cylindered rotary compressor.
  • JP S63 126580 discloses a two-cylindered rotary compressor.
  • US 2010/147013 discloses a multi-cylinder rotary compressor and refrigeration cycle equipment.
  • the points for increasing the efficiency of the multi-cylinder rotary compressors are as follows. (1) To reduce leakage loss by making the cylinder width (thickness) small, and shortening the axial seal length between the outer peripheral surface of the rotor and the inner peripheral surface of the cylinder, and (2) To make the diameter of a journal part, the diameter of an eccentric shaft part, and the external diameter of the rotor small, respectively, and reduce the sliding loss during the rotation of the rotor.
  • the invention has been made in view of such circumstances, and an object thereof is to provide a rotary compressor that removes restrictions on intake pipe diameter, seal limits on a separator plate, assembly limits on a rotating shaft, and the like, makes possible a design with limitations exceeding that of the present situation, and achieves increased efficiency, a reduced number of components, and simplified assembly.
  • the rotary compressor of the invention adopts the following means. That is, the multi-cylinder rotary compressor related to the invention is a multi-cylinder rotary compressor including a plurality of cylinders.
  • a rotating shaft provided with a plurality of eccentric shaft parts at predetermined intervals in an axial direction is divided by a center shaft part between the eccentric shaft parts into a rotating shaft having a divided structure that can be integrally linked.
  • the plurality of cylinders has cylinder chambers formed in both end surfaces, resulting in an integrated-structure cylinder in which a separator plate partitioning the cylinder chambers is integrally formed in the center.
  • the eccentric shaft parts can be easily assembled without being passed through the through-hole of the separator plate by passing the center shaft part of the rotating shaft having the divided structure through the through-hole of the separator plate, and then integrally linking the center shaft part with the through-hole. Additionally, even if leakage loss is reduced by making the width (thickness) small, the width (thickness) of the integrated-structure cylinder can be increased by the thickness of the separator plate, and an intake port and an intake pipe connection hole can be provided within the increased cylinder width (thickness).
  • an intake port and an intake pipe connection hole that extend radially outward from each of the cylinder chambers may be provided in the integrated-structure cylinder, and at least a portion from one end of a peripheral region around the intake port and the intake pipe connection hole to the other end thereof may be a continuous wall.
  • an intake port and an intake pipe connection hole with larger diameter can be provided without being restricted by the width of the individual cylinder. Therefore, even if the cylinder width is made small, the diameter of the intake port or the pipe diameter of the intake pipe is not restricted, a problem such that intake efficiency is lowered due to an increase in pressure loss can be solved, and increased efficiency can be achieved.
  • the plurality of cylinder chambers of which both ends are closed may be formed by bearing members being installed in both end surfaces of the integrated-structure cylinder, and the rotating shaft may be rotatably supported via the bearing members in both the end surfaces.
  • the plurality of cylinder chambers of which both ends are closed by the integrally formed separator plate can be formed by installing the bearing members, respectively, in both the end surfaces of the integrated-structure cylinder, and the rotating shaft can be rotatably supported via the pair of bearing members. Therefore, compared to a multi-cylinder rotary compressor of a related-art type in which a separator plate that is a separate component is sandwiched and assembled between a plurality of cylinders having separate configurations, and bearing members are incorporated into both ends of the separator plate, the number of components can be reduced, and simplification of the configuration and assembly of the components, downsizing, and the like can be achieved.
  • a plurality of intake ports and intake pipe connection holes may be provided to correspond to the plurality of cylinder chambers.
  • the integrated-structure cylinder is adopted. Accordingly, intake ports and intake pipe connection holes with larger diameter can be provided without being restricted by the width of the individual cylinders. Therefore, even if the cylinder width is made small, the diameter of the intake ports or the pipe diameter of the intake pipes is not restricted, a problem such that intake efficiency is lowered due to an increase in pressure loss can be solved, and increased efficiency can be achieved.
  • the intake port may be one intake port that branches so as to straddle the separator plate and communicate with the plurality of cylinder chambers, and one intake pipe connection hole may be provided to communicate with the intake port.
  • the one larger common intake port and the one intake pipe connection hole communicating with this common intake port can be provided in the integrated-structure cylinder corresponding to the width of the plurality of cylinders. Accordingly, refrigerant gas can be made to be taken into the plurality of cylinder chambers via the intake port having the branch configuration. Therefore, even if the cylinder width is made small, the diameter of the intake port or the pipe diameter of the intake pipe is not restricted, a problem such that intake efficiency is lowered due to an increase in pressure loss can be solved, increased efficiency can be achieved, and the simplification of configuration and cost reduction can be achieved by making an intake pipe system a single system.
  • the intake port may be one intake port that communicates with the plurality of cylinder chambers so as to straddle the separator plate, and one intake pipe connection hole may be provided in communication with the intake port.
  • the one larger common intake port and the one intake pipe connection hole communicating with this common intake port can be provided in the integrated-structure cylinder corresponding to the width of the plurality of cylinders. Accordingly, refrigerant gas can be made to be taken into the plurality of cylinder chambers via the intake port having a size so as to straddle the separator plate. Therefore, even if the cylinder width is made small, the diameter of the intake port or the pipe diameter of the intake pipe is not restricted, a problem such that intake efficiency is lowered due to an increase in pressure loss can be solved, increased efficiency can be achieved, and the simplification of configuration and cost reduction can be achieved by making an intake pipe system a single system.
  • the eccentric shaft parts can be easily assembled without being passed through the through-hole of the separator plate by passing the center shaft part of the rotating shaft having the divided structure through the through-hole of the separator plate, and then integrally linking the center shaft part with the through-hole. Additionally, even if leakage loss is reduced by making the cylinder width (thickness) small, the width (thickness) of the integrated-structure cylinder can be increased by the thickness of the separator plate, and the intake port and the intake pipe connection hole can be provided within the increased cylinder width (thickness).
  • FIG. 1 A longitudinal sectional view of a rotary compressor related to the first embodiment of the invention is illustrated in Fig. 1 .
  • a rotary compressor 1 of the present embodiment can be applied to a single-stage multi-cylinder rotary compressor or a multi-stage rotary compressor, and a two-cylinder type hermetic rotary compressor provided with two cylinders is illustrated herein.
  • the rotary compressor 1 is provided with a sealed housing 2, and has a configuration in which a rotary compression mechanism 7 driven via a rotating shaft (crankshaft) 3 by a motor (not illustrated) provided at an upper part within the sealed housing 2 is provided in a lower part in the sealed housing 2.
  • the rotating shaft (crankshaft) 3 has an upper part inked with a rotor of the electric motor and is rotationally driven by the electric motor, and has first and second eccentric shaft parts (crank part) 4 and 5 provided at a lower part thereof so as to shift from each other with a phase of about 180 degrees in two upper and lower places at a predetermined interval.
  • the rotating shaft 3 is divided by a center shaft part 6 between the first and second eccentric shaft parts 4 and 5 into two upper and lower pieces, and is configured such that the eccentric shaft parts are capable of being integrally linked with each other by screw linking or concavo-convex linking.
  • the linking of the rotating shaft 3 divided into two pieces may be performed by means other than the screw linking or the concavo-convex linking.
  • the rotary compression mechanism 7 is provided with an integrated-structure cylinder 11 having a configuration in which a first cylinder 8 is formed in an upper end surface, a second cylinder 9 is formed in a lower end surface, and a separator plate 10 partitioning the first cylinder 8 and the second cylinder 9 is integrally formed in the center.
  • the separator plate 10 is provided with a through-hole 12 having a diameter such that at least the center shaft part 6 of the rotating shaft 3 is capable of passing through the through-hole.
  • the upper bearing member 13 and the lower bearing member 14 rotatably support lower regions of the rotating shaft 3 in two upper and lower places with the integrated-structure cylinder 11 interposed therebetween.
  • Covers 18 and 19 are respectively and integrally tightened to and formed in outer surfaces of the upper bearing member 13 and the lower bearing member 14 via the plurality of bolts 15, and discharge chambers 20 and 21 that discharge compressed gas are formed in the outer surfaces.
  • the upper bearing member 13 has a configuration in which the rotary compression mechanism 7 is fixed to and installed within the sealed housing 2 by being plug-welded or crimped to an inner peripheral surface of the sealed housing 2 in a plurality of places (for example, three places).
  • the integrated-structure cylinder 11 is fixed to and installed in the upper bearing member 13, and the lower bearing member 14 is fixed to and installed in the integrated-structure cylinder 11.
  • the first and second eccentric shaft parts 4 and 5 provided at the rotating shaft 3 are respectively provided to correspond to the inside of the first cylinder chamber 16 and the inside of the second cylinder chamber 17.
  • Rotors (pistons) 22 and 23 are respectively and rotatably fitted to outer peripheries of the first and second eccentric shaft parts 4 and 5.
  • Rotors 22 and 23 are rotated along inner peripheral surfaces of the first cylinder chamber 16 and the second cylinder chamber 17 by the eccentric rotation of the first and second eccentric shaft parts 4 and 5.
  • blade grooves are respectively provided to correspond to the first cylinder chamber 16 and the second cylinder chamber 17, as being publicly known, in the integrated-structure cylinder 11. Blades (not illustrated) that slide in the blade grooves are assembled into the blade grooves in a state where the blades are pressed against and biased to outer peripheries of the rotors 22 and 23.
  • the inside of the first cylinder chamber 16 and the inside of the second cylinder chamber 17 are configured so as to be partitioned into a discharge side and an intake side by the blades.
  • a plurality of intake ports 24 and 25 and a plurality of intake pipe connection holes 26 and 27 that extend radially outward from the cylinder chambers 16 and 17 are respectively provided to correspond to the first cylinder chamber 16 and the second cylinder chamber 17 in the integrated-structure cylinder 11.
  • Intake pipes 28 and 29 from an accumulator or the like are configured so as to be connectable to the intake pipe connection holes 26 and 27. Accordingly, low-pressure refrigerant gas is taken into the first cylinder chamber 16 and the second cylinder chamber 17 via the intake ports 24 and 25 from the intake pipes 28 and 29.
  • a peripheral region in which at least the intake ports 24 and 25 and the intake pipe connection holes 26 and 27 are provided is configured such that a cylinder wall from one end of the integrated-structure cylinder 11 to the other end thereof is a continuous wall and intake ports 24 and 25 and intake pipe connection holes 26 and 27 with larger diameter are capable of being drilled therein within the cylinder width (thickness) without being restricted by the width (thickness) of the first cylinder chamber 16 and the second cylinder chamber 17.
  • the integrated-structure cylinder 11 may be adapted so as to provide cutout parts or thickness-reducing parts in other parts than the intake ports 24 and 25 and the intake pipe connection holes 26 and 27 and further the parts in which the above blade grooves are provided and to reduce material cost or weight.
  • the low-pressure refrigerant gas taken into the first cylinder chamber 16 and the second cylinder chamber 17 through the intake ports 24 and 25 from the intake pipes 28 and 29 is compressed when the rotating shaft 3 is rotationally driven, and the rotors 22 and 23 are eccentrically rotated along the inner peripheral surfaces of the first cylinder chamber 16 and the second cylinder chamber 17 along with this.
  • the gas compressed to a set pressure is discharged into the discharge chambers 20 and 21 via discharge valves and discharge ports, which are not illustrated, is discharged into the sealed housing 2 from the discharge chambers, and is then delivered to the outside of the compressor 1.
  • the rotating shaft 3 provided with the plurality of eccentric shaft parts 4 and 5 at predetermined intervals in the axial direction is divided by the center shaft part 6 between the eccentric shaft parts 4 and 5 into upper and lower pieces and into a rotating shaft 3 having a divided structure that can be integrally linked.
  • the plurality of first cylinder 8 and second cylinder 9 have the first cylinder chamber 16 and the second cylinder chamber 17 formed in both end surfaces, and are configured as the integrated-structure cylinder 11 in which the separator plate 10 partitioning the cylinder chambers 16 and 17 is integrally formed in the center.
  • the eccentric shaft parts 4 and 5 can be easily assembled without being passed through the through-hole 12 of the separator plate 10 by passing the center shaft part 6 of the rotating shaft 3 having the divided structure through the through-hole 12 of the separator plate 10, and then integrally linking the center shaft part with the through-hole.
  • the width (thickness) of the respective cylinders 8 and 9 can be increased by the thickness of the separator plate 10, and the intake ports 24 and 25 and the intake pipe connection holes 26 and 27 can be provided within the increased cylinder width (thickness). Therefore, it is possible to set the diameter of the intake ports 24 and 25 or the pipe diameter of the intake pipes 28 and 29 without being restricted by the cylinder width.
  • the present embodiment has a configuration in which the plurality of first cylinder chamber 16 and second cylinder chamber 17 of which both ends are closed by installing the upper bearing member 13 and the lower bearing member 14 are formed in both the end surfaces of the integrated-structure cylinder 11, and the rotating shaft 3 is rotatably supported by the upper bearing member 13 and the lower bearing member 14 on both the end surfaces.
  • the plurality of first cylinder chamber 16 and second cylinder chamber 17 of which both ends are closed by the integrally formed separator plate 10 can be formed by installing the upper bearing member 13 and the lower bearing member 14 in both the end surfaces of the integrated-structure cylinder 11, and the rotating shaft 3 can be rotatably supported by the pair of upper bearing member 13 and lower bearing member 14.
  • the intake ports 24 and 25 and the intake pipe connection holes 26 and 27 that extend radially outward from the cylinder chambers 16 and 17 are provided in the integrated-structure cylinder 11, and at least a portion from one end of a peripheral region around the intake ports and the intake pipe connection holes to the other end thereof is configured as a continuous wall.
  • intake ports 24 and 25 and intake pipe connection holes 26 and 27 with larger diameter can be provided without being restricted by the width (thickness) of the first cylinder 8 and the second cylinder 9.
  • the plurality of intake ports 24 and 25 and the plurality of intake pipe connection holes 26 and 27 are provided to correspond to the plurality of cylinder chambers 16 and 17. For this reason, even in a configuration in which the plurality of intake ports 24 and 25 and intake pipe connection holes 26 and 27 are provided to correspond to the plurality of cylinder chambers 16 and 17, the integrated-structure cylinder 11 is adopted. Accordingly, intake ports 24 and 25 and intake pipe connection holes 26 and 27 with larger diameter can be provided without being restricted by the respective cylinder width (thickness).
  • the present embodiment is different from the above-described first embodiment in the configuration of an intake port 30 and an intake pipe connection hole 31. Since the other points are the same as those of the first embodiment, the description thereof will be omitted.
  • one thick intake pipe 32 is made connectable by providing one large common intake port 30 that branches so as to straddle the separator plate 10 and communicate with the plurality of cylinder chambers 16 and 17 and by providing one large common intake pipe connection hole 31 communicating with the intake port 30.
  • the intake port 30 into the one common intake port 30 that branches so as to straddle the separator plate 10 and communicates with the plurality of cylinder chambers 16 and 17 and by providing the one common intake pipe connection hole 31 communicating with the intake port 30, the one larger common intake port 30 and the one intake pipe connection hole 31 communicating with this common intake port can be provided in the integrated-structure cylinder 11 corresponding to the width of the plurality of cylinders, and refrigerant gas can be made to be taken into the plurality of cylinder chambers 16 and 17 via the larger intake port 30 having the branch configuration.
  • the present embodiment is different from the above-described first embodiment in the configuration of an intake port 33 and an intake pipe connection hole 34. Since the other points are the same as those of the first embodiment, the description thereof will be omitted.
  • one thick intake pipe 35 is made connectable by providing one large common intake port 33 communicating with the plurality of cylinder chambers 16 and 17 so as to straddle the separator plate 10 and providing one large common intake pipe connection hole 34 communicating with the intake port 33.
  • the intake port 33 into the one common intake port 33 communicating with the plurality of cylinder chambers 16 and 17 so as to straddle the separator plate 10 and by providing the one common intake pipe connection hole 34 communicating with the intake port 33, the one larger common intake port 33 and the one intake pipe connection hole 34 communicating with this common intake port can be provided in the integrated-structure cylinder 11 corresponding to the width of the plurality of cylinders, and refrigerant gas can be made to be taken into the plurality of cylinder chambers 16 and 17 via the single larger intake port 33.
  • the invention is not limited to the inventions related to the above embodiments, and appropriate changes can be made without departing from the scope of the invention.
  • the integrated-structure cylinder 11 is installed in the resulting sealed housing with the bolts 15, and the lower bearing member 14 is installed in the integrated-structure cylinder 11 with the bolts 15 has been described in the above embodiment.
  • the invention is not limited to this.
  • a configuration may be adopted in which the integrated-structure cylinder 11 is fixed to and installed in the sealed housing 2, and the upper bearing member 13 and the lower bearing member 14 are fixed and installed with the bolts 15.
  • the single-stage multi-cylinder rotary compressor 1 has been described. However, it is natural that the rotary compressor 1 may be applied to a multi-stage rotary compressor in which one cylinder of the first cylinder 8 and the second cylinder 9 is a low-stage compressing cylinder, and the other cylinder is a high-stage compressing cylinder.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP14849841.3A 2013-09-27 2014-08-20 Rotary compressor Active EP3015712B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013201575A JP6045468B2 (ja) 2013-09-27 2013-09-27 ロータリ圧縮機
PCT/JP2014/071702 WO2015045678A1 (ja) 2013-09-27 2014-08-20 ロータリ圧縮機

Publications (3)

Publication Number Publication Date
EP3015712A1 EP3015712A1 (en) 2016-05-04
EP3015712A4 EP3015712A4 (en) 2016-05-11
EP3015712B1 true EP3015712B1 (en) 2019-05-01

Family

ID=52742832

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14849841.3A Active EP3015712B1 (en) 2013-09-27 2014-08-20 Rotary compressor

Country Status (4)

Country Link
EP (1) EP3015712B1 (zh)
JP (1) JP6045468B2 (zh)
CN (1) CN105392995B (zh)
WO (1) WO2015045678A1 (zh)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104791249A (zh) * 2015-04-15 2015-07-22 广东美芝制冷设备有限公司 压缩机构部及具有其的双缸旋转式压缩机
CN105065278B (zh) * 2015-07-24 2017-08-25 郑州凌达压缩机有限公司 一种压缩机及其泵体与外壳的组合结构和装配方法
JP6570930B2 (ja) 2015-09-09 2019-09-04 三菱重工サーマルシステムズ株式会社 ロータリ圧縮機およびその製造方法
EP3434902B1 (en) * 2016-03-25 2020-10-07 Toshiba Carrier Corporation Hermetic rotary compressor and refrigeration cycle device
CN106246551B (zh) * 2016-09-18 2018-04-13 珠海格力节能环保制冷技术研究中心有限公司 曲轴、泵体组件和压缩机
US11105331B2 (en) 2016-12-05 2021-08-31 Green Refrigeration Equipment Engineering Research Center of Zhuhai Gree Co., Ltd Cylinder, pump body assembly, compressor, and temperature adjusting device
CN106523363B (zh) * 2017-01-03 2019-01-08 珠海格力节能环保制冷技术研究中心有限公司 一种压缩机、压缩机泵体及调温设备
CN110296081A (zh) * 2019-06-21 2019-10-01 珠海格力节能环保制冷技术研究中心有限公司 泵体组件、压缩机及泵体组件的装配方法

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63126580A (ja) * 1986-11-18 1988-05-30 Isuzu Motors Ltd ポリジシクロペンタジエンを主原料とする樹脂の反応射出成形品の塗装方法
JPS63126580U (zh) * 1987-02-13 1988-08-18
JPH03222887A (ja) * 1990-01-25 1991-10-01 Mitsubishi Heavy Ind Ltd ２気筒ロータリ圧縮機
CN1324240C (zh) * 1998-02-13 2007-07-04 松下电器产业株式会社 气密压缩机
KR100432115B1 (ko) * 2000-10-30 2004-05-17 가부시키가이샤 히타치세이사쿠쇼 복수 실린더 로터리 압축기
JP5117503B2 (ja) * 2007-08-28 2013-01-16 東芝キヤリア株式会社 多気筒回転式圧縮機及び冷凍サイクル装置
JP2010121481A (ja) * 2008-11-18 2010-06-03 Mitsubishi Electric Corp ロータリ圧縮機
JP5341031B2 (ja) * 2010-06-30 2013-11-13 三菱電機株式会社 多気筒回転式圧縮機、その組み立て方法及びその製造装置
CN102748289A (zh) * 2011-04-19 2012-10-24 广东美芝制冷设备有限公司 双缸旋转式压缩机

Non-Patent Citations (1)

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

Also Published As

Publication number Publication date
CN105392995A (zh) 2016-03-09
JP6045468B2 (ja) 2016-12-14
CN105392995B (zh) 2018-04-27
EP3015712A4 (en) 2016-05-11
JP2015068211A (ja) 2015-04-13
WO2015045678A1 (ja) 2015-04-02
EP3015712A1 (en) 2016-05-04

Similar Documents

Publication Publication Date Title
EP3015712B1 (en) Rotary compressor
KR101673739B1 (ko) 전동 압축기
KR101192649B1 (ko) 피스톤 작동을 구비하는 출력 조절 조립체를 가진 압축기
US9435342B2 (en) Horizontal type scroll compressor
US9528514B2 (en) Gas compressor having an asymmetric cylinder chamber
EP2749735B1 (en) Compressor
JP2007113542A (ja) 密閉形２段ロータリ圧縮機
US11022118B2 (en) Concentric vane compressor
JP2013256906A (ja) ロータリ式圧縮機
JP5535511B2 (ja) 密閉型流体機械の製造方法および密閉型流体機械
EP2549109B1 (en) Scroll compressor
JP6127722B2 (ja) 回転式圧縮機
JP5766166B2 (ja) 回転圧縮機
EP3141754B1 (en) Rotary compressor and method for manufacturing the same
JP5606422B2 (ja) 回転圧縮機
EP3141755B1 (en) Rotary compressor
EP2749736B1 (en) Compressor
KR200392423Y1 (ko) 복식 로터리 압축기의 실링구조
KR101418288B1 (ko) 밀폐형 압축기
KR20060087259A (ko) 복식 로터리 압축기의 압축기구부 조립 구조
CN109595166B (zh) 压缩机
JP2014070619A (ja) 回転圧縮機
WO2016110982A1 (ja) 多気筒密閉型圧縮機
EP3647595B1 (en) Rotary compressor
KR20060087257A (ko) 복식 로터리 압축기의 압축기구부 조립 구조

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20160125

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

A4 Supplementary search report drawn up and despatched

Effective date: 20160408

RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 18/356 20060101ALI20160404BHEP

Ipc: F04C 23/00 20060101AFI20160404BHEP

Ipc: F04C 29/00 20060101ALI20160404BHEP

DAX Request for extension of the european patent (deleted)
RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MITSUBISHI HEAVY INDUSTRIES THERMAL SYSTEMS, LTD.

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 18/356 20060101ALI20181210BHEP

Ipc: F04C 23/00 20060101AFI20181210BHEP

Ipc: F04C 29/00 20060101ALI20181210BHEP

INTG Intention to grant announced

Effective date: 20190108

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 1127295

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190515

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602014045980

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190501

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190801

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190901

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190801

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190802

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1127295

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190901

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602014045980

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

26N No opposition filed

Effective date: 20200204

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190831

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190820

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190831

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20190831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190820

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20140820

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190501

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 602014045980

Country of ref document: DE

Representative=s name: CBDL PATENTANWAELTE GBR, DE

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20230703

Year of fee payment: 10

Ref country code: DE

Payment date: 20230627

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20240627

Year of fee payment: 11