EP2093525A2 - Compresseur de type hermétique - Google Patents

Compresseur de type hermétique Download PDF

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Publication number
EP2093525A2
EP2093525A2 EP09250201A EP09250201A EP2093525A2 EP 2093525 A2 EP2093525 A2 EP 2093525A2 EP 09250201 A EP09250201 A EP 09250201A EP 09250201 A EP09250201 A EP 09250201A EP 2093525 A2 EP2093525 A2 EP 2093525A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
electric motor
cylinder
type compressor
mechanism portion
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.)
Granted
Application number
EP09250201A
Other languages
German (de)
English (en)
Other versions
EP2093525A3 (fr
EP2093525B1 (fr
Inventor
Koichi Sato
Hideaki Maeyama
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 Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP2093525A2 publication Critical patent/EP2093525A2/fr
Publication of EP2093525A3 publication Critical patent/EP2093525A3/fr
Application granted granted Critical
Publication of EP2093525B1 publication Critical patent/EP2093525B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type
    • 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
    • F04C18/3562—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/70—Safety, emergency conditions or requirements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/12—Inflammable refrigerants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/902—Hermetically sealed motor pump unit

Definitions

  • the present invention relates to, for example, a hermetic type compressor that can preferably be utilized in refrigerating apparatus, air-conditioning apparatus, and hot water supplying apparatus.
  • the refrigerating cycle apparatus comprises: a main refrigerant circuit connected via piping to a compressor and a pressure reducing valve, which infuses a main refrigerant inside; a use side refrigerant circuit connected via piping to an use side heat exchanger and an use side pump, which infuses a use side refrigerant inside; a heat source side refrigerant circuit connected via piping to a heat source side heat exchanger and a heat source side pump, which infuses a heat source side refrigerant inside; a use side intermediate heat exchanger connected to each of the main refrigerant circuit and the use side refrigerant circuit, which performs a heat exchange between the main refrigerant and the use side refrigerant; and a heat source side intermediate heat exchanger connected to each of the main refrigerant circuit and the heat source side refrigerant circuit, which performs a heat exchange between the main refrigerant and the use side refrigerant; and a heat source side intermediate heat exchanger connected to each of the main refrig
  • the refrigerating cycle apparatus is proposed, in which the use side pump is driven by the same drive mechanism that drives the compressor, in an attempt to reduce a size of the device.
  • an outer diameter of the drive mechanism part is less than an outer diameter of the compressor (for example, refer to patent document 1).
  • Patent Document 1 Japanese Unexamined Patent Publication No. 200-65431 (page 7, Fig. 2 )
  • Patent Document 2 Japanese Unexamined Patent Publication No. 05-302584
  • a natural refrigerant such as HC (hydrocarbon) refrigerant or R717 (ammonia)
  • HC refrigerant includes: a single refrigerant, such as R170 (ethane), R1270 (propylene), R290 (propane), and R600a (isobutane) ; and combination of these refrigerants.
  • the hermetic type compressor being adopted in the refrigerating apparatus, the air-conditioning apparatus, the hot water supplying apparatus, or the like, is of a high-pressure type inside a hermetic container. For this reason, in order to decrease the amount of refrigerant to be infused into the refrigerant circuit, it is necessary to reduce an inner space volume of the hermetic container of the hermetic type compressor.
  • abnormal vibrations and noises are generated from the compressing mechanism portion and the electric motor, or their operation may fail in the worst case, if a coaxialty is not secured within a prescribed value, between an electric motor stator fixed to the hermetic container covering the electric motor and a rotor fixed to a drive shaft of the compressing mechanism portion which is rotably held in position to the compressing mechanism portion.
  • the hermetic container covering the compressing mechanism portion and the hermetic container covering the electric motor should be manufactured under a highly precise coaxial assembly technology, which prominently deteriorates the production yield, and the production cost becomes expensive.
  • a rotary compressor of the patent document 2 has the following problems.
  • R410 refrigerant has been used as the refrigerant of a conventional air-conditioning apparatus. If the HC refrigerant is used by replacing with the R410 refrigerant, given that geometric displacements of their compressing mechanism portions are identical, a refrigerating capacity declines down to about 10%, owing to the properties of the refrigerant. For example, provided that a refrigerating capacity is A when the R410A refrigerant is in use, and if a hermetic type compressor that uses the HC refrigerant is produced at the identical geometric displacement, its refrigerating capacitywill be 0.9 XA. There is a need to increase the geometric displacement by 10% in order to obtain the identical refrigerating capacity as the conventional R410A refrigerant.
  • a compression efficiencyof the hermetic type compressor is proportional to a value which divides an inner diameter of the cylinder by a height of the cylinder . That is, the compression efficiency will increase if the inner diameter of the cylinder is relatively greater than the height of the cylinder, that is, if a cylinder dimension is flat. At this time, the inner diameter of the cylinder is increased if the inner diameter of the cylinder and the height of the cylinder are designed in pursue of this efficiency based on the conventional technology.
  • increasing the inner diameter of the cylinder also increases the outer diameter of the cylinder, that is, the inner diameter of the hermetic container covering the cylinder is also increased. If the inner diameter of the hermetic container is increased, an inner diameter of a bottom part of the hermetic container where a refrigerating machine oil is stored for supplying to the compressing mechanism portion is also increased. An amount of the refrigerating machine oil to be infused becomes large if attempt to secure a fixed oil level.
  • the HC refrigerant shows an extremely high solubility to the refrigerating machine oil that is generally being used today.
  • the HC refrigerant readily dissolves in the refrigerating machine oil.
  • the amount of refrigerant to be infused must also be infused by an extra amount of the refrigerant dissolving to the refrigerating machine oil.
  • the refrigerating machine oil has no recycle utility, therefore, it must be discarded.
  • the amount of refrigerating machine oil being infused is large, the amount of refrigerating machine oil to be discarded gets also large, therefore, the effect that gives on the environment is of a concern.
  • the present invention attempts to solve the problems mentioned above.
  • the present invention is directed to provide a safe hermetic type compressor adopted in the refrigerant circuit that uses the HC refrigerant, by decreasing the amount of refrigerant to be infused, so that there is a less chance of the danger such as fire ignition or explosion occurring which may be caused by the refrigerant leakage.
  • a hermetic type compressor using the HC (hydrocarbon) refrigerant comprises, inside a hermetic container, a compressing mechanism portion for compressing the refrigerant and an electric motor for driving the compressing mechanism portion, and performs compression of the refrigerant continuously by dividing a compression room with a vane into a high-pressure room and a low-pressure room.
  • the compression room is composed of a cylinder that disposes therein a rolling piston fitted to an eccentric axis of the crankshaft rotated by the electric motor and a cylinder head and a frame that block both ends of the cylinder in an axial direction.
  • the electric motor is fitted and fixed to an inner peripheral plane of the hermetic container.
  • An outer diameter of the electric motor is less than an outer diameter of the compressing mechanism portion.
  • D/H is set to more than 0.5 and less than 0.6.
  • a safe hermetic type compressor is provided by making the outer diameter of the electric motor smaller than the outer diameter of the compressing mechanism portion, and thereby decreasing the amount of refrigerant to be infused.
  • D/H is set to more than 0.5 and less than 1.6. In this way, even in a case of increasing the geometric displacement capacity, a cylinder shape is elongated without increasing the inner diameter of the cylinder, and an inner diameter of a shell is not increased. The amount of the refrigerant to be infused is less.
  • the refrigerating machine oil to be infused is less. Accordingly, even in the case of refrigerant leakage, there is a less chance of danger such as fire ignition or explosion occurring, and the hermetic type compressor having reduced an influence that gives to the environment upon dismantling is provided.
  • Figs. 1 and 2 illustrate the first embodiment.
  • Fig. 1 schematically shows the longitudinal section of the hermetic type compressor 100.
  • Fig. 2 shows the longitudinal section of the essential parts of the hermetic type compressor 100.
  • the hermetic type compressor 100 will be described with reference to Fig. 1 .
  • the hermetic type compressor 100 is described by using the rotary compressor as one example. However, besides the rotary compressor, it is also applicable to a scroll compressor.
  • the hermetic type compressor 100 stores a compressing mechanism portion 20 and an electric motor 10 for driving the compressing mechanism portion 20, inside the hermetic compressor 1.
  • the electric motor 10 includes a stator 2 and a rotor 3 that rotates at an inner side of the stator 2. An electric power is supplied to the stator 2 from a glass terminal 30.
  • a brushless DC motor, an induction electric motor, or the like is normally used.
  • the compressingmechanismportion 20 includes a cylinder 16. An outer peripheral part of the cylinder 16 is fixed to an inner wall of the hermetic container 1. Inside the cylinder 16, there is a space in which both end faces are opened in the axial direction. A rolling piston 7 is stored in this space. The rolling piston 7 is fitted to an eccentric axis 6a of the crankshaft 6, for eccentric revolution inside the cylinder 16.
  • the frame 5 is also called an upper bearing, and supports the crankshaft 6.
  • the cylinder head 4 is also called a lower bearing, and supports the crankshaft 6.
  • a vane is slidably incorporated to a groove (not illustrated) of the cylinder 16, to separate a high-pressure side and a low-pressure side of the compression room by regularly contacting an outer periphery of the rolling piston 7.
  • a refrigerating machine oil 40 is collected at the bottom part of the hermetic container 1, which is to be guided to an inside of the rolling piston 7 via inside of the crankshaft 6.
  • a suction muffler 22 is fixed to an outside of the hermetic container 1.
  • a refrigerant gas (lower pressure and low temperature) is absorbed from the refrigerant circuit (not illustrated) through an absorbing pipe 23 installed at an upper part of the suction muffler 22.
  • the absorption gas is supplied to the compression room of the compressing mechanism portion 20 via a lower connection pipe 24 installed at a lower end of the suction muffler 22.
  • a high temperature and high pressure discharge gas compressed at the compressing mechanism portion 20 is discharged inside the hermetic container 1, and released to the refrigerant circuit (not illustrated) from a discharge pipe 25, afterpassing through the electric motor 10.
  • the compression efficiency of the hermetic type compressor 100 that is, a ratio of an actual refrigerating capacity to a theoretical refrigerating capacity declines in a compressing step of the hermetic type compressor 100. This is because the actual refrigerating capacity declines if the amount of refrigerant gas leaking from a high-pressure side to a low-pressure side increases. The amount of refrigerant leaking from the high-pressure side to the lower-pressure side in this compressing step is proportional to the height of the cylinder.
  • a flow area of the refrigerant gas leaking from the high-pressure side to the low-pressure side is reduced by that amount, and the decline in the refrigerating capacity is eased. Due to this, as for the conventional compressor, in many cases, a value which divides the inner diameter D of the cylinder by the height H of the cylinder is 1.6 and more.
  • the inner diameter of the cylinder is increased, the inner diameter D of the bottom part of the hermetic container 1 where the refrigerating machine oil 40 is stored for supplying to the compressing mechanism portion 20 is also increased.
  • An amount of the refrigerating machine oil to be infused becomes large if attempt to secure a fixed oil level.
  • the HC refrigerant shows an extremely high solubility to the refrigerating machine oil 40 that is generally being used today.
  • the HC refrigerant readily dissolves in the refrigerating machine oil 40.
  • the amount of refrigerant to be infused must also be infused by an extra amount of the refrigerant dissolving to the refrigerating machine oil 40.
  • the refrigerating machine oil 40 has no recycle utility, therefore, it must be discarded.
  • the amount of refrigerating machine oil 40 to be infused is large, the amount of refrigerating machine oil 40 to be discarded gets also large, therefore, the effect that gives on the environment is intense.
  • D/H is set to more than 0.5 and less than 1.6, which is a value that divides the inner diameter D of the cylinder 16 by the height of the cylinder. Therefore, the cylinder 16 has an elongated shape, and the inner diameter D of the cylinder is not increased, and the inner diameter of the hermetic container 1 is also not increased.
  • a safe hermetic type compressor for the cylinder having the inner diameter D and the height H, D/H is set to more than 0.5 and less than 1.6. Based on this, even in a case of increasing the geometric displacement capacity, the cylinder shape is elongated without increasing the inner diameter of the cylinder, and the inner diameter D of the hermetic container 1 is not increased. The amount of the refrigerant to be infused is less. The refrigerant machine oil to be infused is also less. Accordingly, even in the case of refrigerant leakage, there is a less chance of danger such as fire ignition or explosion occurring, and the hermetic type compressor having reduced an influence that gives to the environment upon dismantling is provided.
  • Fig. 3 illustrates the second embodiment.
  • Fig. 3 schematically shows a longitudinal section of the hermetic type compressor 100.
  • Aconfigurationof the hermetic type compressor 100 shown in Fig. 3 is the same as the hermetic type compressor 100 of Fig. 1 .
  • the electric motor 10 is fitted and fixed to the inner periphery of the hermetic container 1 by shrink fitting the electric motor 10.
  • An output of the electric motor 10 of the hermetic type compressor 100 is described herein.
  • a normal hermetic type compressor 100 even if a refrigerant in use has changed, in terms of restriction inproduction facility, the same compressing mechanism portion 20 and the electric motor 10 are used in most cases.
  • the R410A refrigerant had been used in air conditioners. If the HC refrigerant is used instead of the R410A refrigerant, given that the geometric displacement of the compressing mechanism portions 20 are identical, its refrigerating capacity declines down to about 10%, owing to the properties of the refrigerant.
  • the geometric displacement is a geometrical volume to be displaced per 1 rotation of the hermetic type compressor 100.
  • an output of the electric motor 10 is A when the R410A refrigerant is being used, if the hermetic type compressor 100 using the HC refrigerant at the identical geometric displacement is produced, the required output generated by the electric motor 10 at that time is 10% less than the conventional output, 0.9 X A, and a difference 0.1 X A becomes an excess.
  • the outer diameter Dm of the electric motor 10 is decreased, which is made smaller than the outer diameter Dc of the compressing mechanism portion 20.
  • the output of the electric motor 10 is adjusted by reducing the capacity, that is, by decreasing an outer diameter of the core 2a used by the electric motor 10. In this case, a length in the axial direction of the core 2a (the core width) is fixed.
  • the output of the electric motor 10 is assumed to be proportional to a volume of the core 2a (all of the stators and rotors). Since the core width is fixed, if the required output generated by the electric motor 10 is 10% less than the conventional output, 0.9 X A, then the outer diameter of the electric motor 10 can be decreased to ⁇ 0.9 ⁇ 0.95Dm. Since the outer diameter of the electric motor 10 is the same as the inner diameter of the hermetic container 1 of the part 1b covering the electric motor 10, the inner diameter of the hermetic container 1 of the part 1b covering the electric motor 10 can be decreased down to approximately 5%. In this way, the inner capacity of the hermetic container 1 is decreased.
  • the second embodiment has the following effects. That is, since the outer diameter Dm of the electric motor 10 is reduced with respect to the outer diameter Dc of the compressing mechanism portion 20, the space volume of the hermetic container 1 is reduced, and thereby decreasing the amount of refrigerant to be infused. Thus, even if a highly inflammable refrigerant is being used, there is a less chance of danger such as fire ignition or explosion occurring upon the refrigerant leakage, and a safe hermetic type compressor 100 is effectively obtained.
  • the container covering the compressing mechanism portion, the container covering the electric motor, and the container covering the heat source side pump are separately configured. Furthermore, inside the electric motor, the stators are separated by the cans.
  • the main refrigerant having the toxic and inflammable properties does not exist at a stator area. Accordingly, the amount of the main refrigerant having the toxic and inflammable properties cannot be decreased even if the electric motor is reduced.
  • the outer diameter Dm of the electric motor 10 is reduced with respect to the outer diameter Dc of the compressing mechanism portion 20.
  • a width of the core 2a of the electric motor 10 (the length in the axial direction) of the present embodiment is reduced with respect to a width of the core 2a of the electric motor 10 being set to the conventional refrigerant such as R410A.
  • the output of the electric motor 10 of the present embodiment is adjusted by decreasing the volume of the core 2a, which is used by the electric motor 10. Accordingly, a height of the hermetic container 1 that covers the electric motor 10 is lowered. In this way, the inner volume of the hermetic container 1 is reduced.
  • An output of the electric motor 10 is assumed to be proportional to the volume of the core 2a (all of the stators and rotors). Since the outer diameter of the electric motor 10 is fixed, if the required output generated by the electric motor 10 is 10% less than the conventional output, 0.9 X A, then a core width H of the electric motor 10 can also be decreased to 0.9H.
  • the highly-pressurized space is reduced, and the amount of refrigerant to be infused into the refrigerant circuit can be decreased.
  • the width of the core 2a of the electric motor 10 is reduced with respect to the width of the core 2a of the electric motor 10 set for the conventional refrigerant such as R410A. Therefore, a space volume inside of the hermetic container 1 can be reduced, and thereby decreasing the amount of refrigerant to be infused. Thus, even if a highly inflammable refrigerant is being used, there is a less chance of the danger such as fire ignition or explosion occurring upon the refrigerant leakage, and a safe hermetic compressor 100 is effectively obtained.
  • hermetic type compressor 100 can be configured by combining the first, second and third embodiments.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
EP09250201.2A 2008-02-20 2009-01-26 Compresseur de type hermétique Active EP2093525B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2008038860A JP5132351B2 (ja) 2008-02-20 2008-02-20 密閉型圧縮機

Publications (3)

Publication Number Publication Date
EP2093525A2 true EP2093525A2 (fr) 2009-08-26
EP2093525A3 EP2093525A3 (fr) 2014-11-26
EP2093525B1 EP2093525B1 (fr) 2018-01-10

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EP (1) EP2093525B1 (fr)
JP (1) JP5132351B2 (fr)
KR (1) KR101064374B1 (fr)
CN (1) CN101514696B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150204587A1 (en) * 2014-01-23 2015-07-23 Samsung Electronics Co., Ltd. Cooling apparatus and compressor

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102748288A (zh) * 2011-04-22 2012-10-24 广东美芝制冷设备有限公司 使用r290冷媒的旋转式压缩机
JP2017172348A (ja) * 2016-03-18 2017-09-28 日立ジョンソンコントロールズ空調株式会社 容積形圧縮機

Citations (2)

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Publication number Priority date Publication date Assignee Title
JPH05302584A (ja) 1992-04-23 1993-11-16 Hitachi Ltd ロータリ圧縮機
JP2000065431A (ja) 1998-08-24 2000-03-03 Matsushita Electric Ind Co Ltd 冷凍サイクル装置および冷凍サイクル装置用圧縮機

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US20150204587A1 (en) * 2014-01-23 2015-07-23 Samsung Electronics Co., Ltd. Cooling apparatus and compressor
EP2908071A1 (fr) * 2014-01-23 2015-08-19 Samsung Electronics Co., Ltd Appareil de refroidissement et compresseur
US10365021B2 (en) 2014-01-23 2019-07-30 Samsung Electronics Co., Ltd. Cooling apparatus and compressor

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EP2093525A3 (fr) 2014-11-26
KR20090090265A (ko) 2009-08-25
JP5132351B2 (ja) 2013-01-30
KR101064374B1 (ko) 2011-09-14
CN101514696B (zh) 2011-06-22
CN101514696A (zh) 2009-08-26
EP2093525B1 (fr) 2018-01-10
JP2009197644A (ja) 2009-09-03

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