EP2169232A1 - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
- Publication number
- EP2169232A1 EP2169232A1 EP08710540A EP08710540A EP2169232A1 EP 2169232 A1 EP2169232 A1 EP 2169232A1 EP 08710540 A EP08710540 A EP 08710540A EP 08710540 A EP08710540 A EP 08710540A EP 2169232 A1 EP2169232 A1 EP 2169232A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- housing
- face
- rotary compressor
- rotator
- situated
- 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
Links
- 239000003507 refrigerant Substances 0.000 claims description 40
- 239000000203 mixture Substances 0.000 claims description 25
- 230000006835 compression Effects 0.000 claims description 19
- 238000007906 compression Methods 0.000 claims description 19
- 239000002245 particle Substances 0.000 claims description 8
- 238000004378 air conditioning Methods 0.000 claims description 4
- 238000000926 separation method Methods 0.000 abstract description 10
- 239000003921 oil Substances 0.000 description 37
- 239000000314 lubricant Substances 0.000 description 11
- 238000010586 diagram Methods 0.000 description 6
- 239000000463 material Substances 0.000 description 4
- 229910000976 Electrical steel Inorganic materials 0.000 description 2
- 230000004907 flux Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 229920000728 polyester Polymers 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
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
- 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
-
- 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
- F04C29/02—Lubrication; Lubricant separation
- F04C29/026—Lubricant separation
-
- 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
- F04C29/02—Lubrication; Lubricant separation
- F04C29/023—Lubricant distribution through a hollow driving shaft
Definitions
- the present invention relates to a rotary compressor.
- a rotary compressor is used for compressing a gas refrigerant in a refrigerant circuit in an air conditioning system such as a room air conditioner or a packaged air conditioner.
- a rotary compressor for example, a rotary compressor disclosed in patent document 1 is known.
- Patent document 1 Japanese Unexamined Patent Application, Publication No. 2005-337210
- a plurality of communicating channels are formed in a proximal end of a crossover portion of a stator core situated in the upside, each of which extends along a direction perpendicular to a rotation axis of a crank shaft, and communicates between the inside of a concave portion formed by the crossover portion of the stator core situated in the upside, and the inside of a barrel of a housing.
- the invention was made in the light of the above circumstance, and an object of the invention is to provide a rotary compressor that can improve oil separation efficiency.
- a first aspect of the rotary compressor according to the invention includes a rotary compressor having a housing, a compression mechanism section accommodated in a lower side of the housing, and a drive part accommodated in an upper side of the housing, in which the drive part has a rotator that is fitly fixed around a crank shaft, and rotates with the crank shaft, and a stator that is disposed at an outer circumferential side of the rotator and fixed to the housing, an oil separator plate is attached to an upper end face of a rotor core of the rotator such that the separator plate covers the upper end face, and is situated in a concave portion formed by a crossover portion projecting from an upper end face of a stator core of the stator, and a plurality of communicating channels, which communicates between the inside of the concave portion and the inside of a barrel of the housing, are formed at a proximal end of the crossover portion; wherein the rotator is fixed to the crank shaft such that the
- a covering ratio of the open end, which is situated at the entrance side of the communicating channel, by the side face of the rotor core is 30% to 80%, thereby the amount of mixture leaking (escaping) into the barrel of the housing through the communicating channels can be reduced, and the amount of mixture colliding with the crossover portion can be increased, consequently separation efficiency of oil particles can be improved.
- oil can be prevented from outflowing to the outside of the housing, so that a lubricant can be avoided from being insufficiently supplied to respective components within the housing, consequently life of the rotary compressor can be increased.
- a second aspect of the rotary compressor according to the invention includes a rotary compressor having a housing, a compression mechanism section accommodated in a lower side of the housing, and a drive part accommodated in an upper side of the housing, in which the drive part has a rotator that is fitly fixed around a crank shaft, and rotates with the crank shaft, and a stator that is disposed at an outer circumferential side of the rotator and fixed to the housing, an oil separator plate is attached to an upper end face of a rotor core of the rotator such that the oil separator plate covers the upper end face, and is situated in a concave portion formed by a crossover portion projecting from an upper end face of a stator core of the stator, and a plurality of communicating channels, which communicates between the inside of the concave portion and the inside of a barrel of the housing, are formed at a proximal end of the crossover portion; wherein a closing member is provided over entrance ends and/or exit ends of the communicating channels.
- the closing member is simply used to close the open ends situated at the exit sides of the communicating channels, thereby the amount of mixture leaking (escaping) into the barrel of the housing through the communicating channels can be made zero (or extremely reduced), and the amount of the mixture colliding with the crossover portion can be increased, consequently separation efficiency of oil particles can be improved. Moreover, oil can be prevented from outflowing to the outside of the housing, so that a lubricant can be avoided from being insufficiently supplied to respective components within the housing, consequently life of the rotary compressor can be increased.
- a third aspect of the rotary compressor according to the invention includes a rotary compressor having a housing, a compression mechanism section accommodated in a lower side of the housing, and a drive part accommodated in an upper side of the housing, in which the drive part has a rotator that is fitly fixed around a crank shaft, and rotates with the crank shaft, and a stator that is disposed at an outer circumferential side of the rotator and fixed to the housing, an oil separator plate is attached to an upper end face of a rotor core of the rotator such that the oil separator covers the upper end face, and is situated in a concave portion formed by a crossover portion projecting from an upper end face of a stator core of the stator, and a plurality of communicating channels, which communicate between the inside of the concave portion and the inside of a barrel of the housing, are formed at a proximal end of the crossover portion; wherein the communicating channels are formed such that the amount of a mixture of oil particles and a refrigerant gas out
- the amount of mixture leaking (escaping) into the barrel of the housing through the communicating channels can be zero or extremely reduced (minimized), and the amount of the mixture colliding with the crossover portion can be increased, consequently separation efficiency of oil particles can be improved.
- oil can be prevented from outflowing to the outside of the housing, so that a lubricant can be avoided from being insufficiently supplied to respective components within the housing, consequently life of the rotary compressor can be increased.
- Fig. 1 shows a schematic, vertical section diagram of a rotary compressor according to the embodiment
- Fig. 2 shows an enlarged vertical section diagram of a relevant part of Fig. 1
- Fig. 3 shows a graph showing a relationship between compressor efficiency and a stator-coil gap shielding ratio, and a relationship between system COP and the stator-coil gap shielding ratio in the rotary compressor according to the embodiment.
- a rotary compressor 1 is provided on a refrigerant circuit of an air conditioning system such as a room air conditioner or packaged air conditioner, and used for compressing a gas refrigerant circulating through the refrigerant circuit.
- the rotary compressor 1 has a housing 2 being a closed vessel, and a compression mechanism section 3 for compressing a gas refrigerant supplied from the refrigerant circuit, and a drive part 4 for driving the compression mechanism section 3 are accommodated in the housing 2.
- the housing 2 is formed as an approximately cylindrical, closed vessel being closed at both ends, and installed with an approximately vertical axis.
- the compression mechanism section 3 is disposed in a lower side of the housing 2, and the drive part 4 is disposed above the compression mechanism section 3.
- a lower side-face of the housing 2 is inserted with refrigerant pipes P1 and P2 of the refrigerant circuit from the outside, and the gas refrigerant is supplied from the refrigerant circuit to the compression mechanism section 3 through the refrigerant pipes P1 and P2.
- an oil reservoir room is provided in a bottom of the housing 2, and a lubricant used for lubrication of the compression mechanism section 3 and the like is reserved in the oil reservoir room.
- the compression mechanism section 3 compresses the gas refrigerant supplied through the refrigerant pipes P1 and P2 into a high-pressure compressed gas, then sends out the gas into the housing 2.
- a top of the housing 2 is inserted with a refrigerant pipe P3 from the outside, and the compressed gas being temporarily reserved in the housing 2 is sent to a downstream side of the refrigerant circuit through the refrigerant pipe P3.
- the compression mechanism section 3 has a plurality of cylinders 11 each having a cylindrical inner-face 12, and the cylinders 11 are adjacently disposed in an axial direction in a manner that respective cylindrical inner-faces 12 are approximately coaxial with each other, and a separator 13 is interposed between the cylinders.
- a cylindrical rotor 14 having a smaller diameter than that of each cylindrical inner-face 12 is provided within each of the cylinders 11 with its axis being approximately parallel to an axis of each cylindrical inner-face 12.
- a crank shaft 16 is inserted through the cylinders 11, separator 13, and rotors 14.
- the crank shaft 16 is provided with its axis being approximately parallel to an array direction of the cylinders 11, and inserted into the compression mechanism section 3 at a lower-end side.
- the crank shaft 16 is supported at an upper-end side by the drive part 4, and rotationally driven about the axis by the drive part 4.
- the drive part 4 includes an electromotive motor having a rotor holding the upper-end side of the crank shaft 16, and the rotor is rotated to rotationally drive the crank shaft 16.
- the crank shaft 16 has a region to be inserted into respective cylinders 11, in which approximately cylindrical, eccentric shafts 17 are provided, the shafts being engaged with inner circumferential faces of the rotors 14 respectively, and the crank shaft 16 is rotationally driven about the axis, thereby each rotor 14 is eccentrically rotated in a manner of rolling on the cylindrical inner surface 12 of each cylinder 11.
- the eccentric shafts 17 are provided while eccentric directions thereof are shifted approximately 180 degrees from each other about the axis of the crank shaft 16 (that is, phases are shifted about 180 degrees from each other about the axis).
- crank shaft 16 when the crank shaft 16 is rotationally driven, inertia moment produced in one eccentric shaft 17 and inertia moment produced in the other eccentric shaft 17 are cancelled by each other, so that rotation of the crank shaft 16 is stabilized.
- an array of the cylinders 11 is mounted with end bearings 18 at one end side and at the other end side respectively, and the crank shaft 16 is supported by the end bearings 18 while it can be rotated about the axis.
- the drive part 4 has a rotator 21 being fitly fixed around the crank shaft 16, and a stator 22 arranged at an outer circumferential side of the rotator 21.
- the rotator 21 includes a core (hereinafter, called “rotor core”) 23 formed by stacking a plurality of thin materials such as silicon steel sheets formed in a certain shape, and the rotor core 23 has a plurality of through-holes (hereinafter, called "passages”) 25 extending in a vertical direction along an axial hole 24 of the rotor core.
- Each of the passages 25 has a lower end being an open end, and a mixture of a lubricant, which is for smoothly driving the compression mechanism section 3 and the drive part 4, and the refrigerant gas flows into the passages 25 through the open ends. It is also acceptable that a cylindrical body is fitted in the axial hole 24 of the rotor core 23, and the crank shaft 16 is pressed into the cylindrical body.
- a disk-like oil separator plate 28 is mounted on an upper end face 23a of the rotor core 23 via an attachment stage 26 and fastening members (for example, bolts and nuts) 27 such that the plate 28 covers the upper end face 23a.
- fastening members for example, bolts and nuts
- a plurality of through-holes 29 are provided, which penetrate the stage 26 in a thickness direction, and are adjusted to open ends provided at upsides of the passages 25 respectively.
- the mixture of the lubricant and the refrigerant gas flowing into the passages 25 through the open ends provided at the lower side of the passages 25 outflows to the outside of the rotor core 23 (into a space formed between the upper end face 23a of the rotor core 23 and the oil separator plate 28) through the open ends provided at the upsides of the passages 25 and the through-holes 29 as shown in arrows in full line of Fig. 2 .
- the stator 22 includes a core (hereinafter, called “stator core”) 30 formed by stacking a plurality of thin materials such as silicon steel sheets formed in a certain shape, and coil ends (crossover portions) 31 wind on teeth of the stator core 30.
- stator core 30 formed by stacking a plurality of thin materials such as silicon steel sheets formed in a certain shape, and coil ends (crossover portions) 31 wind on teeth of the stator core 30.
- crossover portions 32 of the coil ends 31 project from either of end faces 30a and 30b of the stator core 30, and thus form upper and lower concave portions 33 and 34 in the compression mechanism section 3.
- the attachment stage 26 and the oil separator plate 28 are accommodated.
- the stator core 30 is fixed by pressing in a barrel 2a of the housing 2 (shrinkage fit).
- a plurality of communicating channels 35 are formed, each of which extends in a direction perpendicular to the rotation axis of the crank shaft 16, and communicates between the inside of the concave portion 33 and the inside of the barrel 2a of the housing 2.
- the rotator 21 is fixed to the crank shaft 16 such that an upper end face 23a of the rotor core 23 is situated at a position upper than the upper end face 30a situated at an upside of the stator core 30, and when an open end situated at an entrance side (inside in a radial direction) of a communicating channel 35 is seen from an open end situated at an exit side (outside in a radial direction) of the same communicating channel 35, a covering (closing) ratio of the open end, which is situated at the entrance side of the communicating channel 35, by a side face 23b of the rotor core 23 (stator-coil gap shielding ratio) is 30% to 80% (most preferably, about 50%).
- the mixture (mixture of the refrigerant gas and the lubricant) rising through the passage 25 outflows into a space formed between the upper end face 23a of the rotor core 23 and the oil separator plate 28. Then, the outflowing mixture is radially scattered (dispersed) to a crossover portion 32 side due to centrifugal force caused by rotation of the oil separator plate 28, and collides with the crossover portion 32.
- the mixture collides with the crossover portion in this way oil in the mixture adheres on a side face of the crossover portion 32, so that the oil is separated from the refrigerant gas.
- the separated oil is returned to the oil reservoir room provided in the lower side of the housing 2 along the stator 22.
- the separated refrigerant gas is discharged to the outside of the housing 2 via the refrigerant pipe P3 provided in a top of the housing 2.
- the stator-coil gap shielding ratio is designed to be 30% to 80%, thereby the amount of mixture leaking (escaping) into the barrel 2a of the housing 2 through the communicating channel 35 can be reduced, and the amount of mixture colliding with the crossover portion 32 can be increased, consequently separation efficiency of oil particles can be improved. As a result, as shown in Fig.
- the refrigerant gas containing oil can be prevented from outflowing into a refrigerant circuit using the rotary compressor 1, consequently system COP of the refrigerant circuit as a whole can be extremely improved.
- oil can be prevented from outflowing to the outside of the housing 2, so that the lubricant can be avoided from being insufficiently supplied to respective components in the housing 2, consequently life of the rotary compressor 1 can be increased.
- FIG. 4 shows a schematic, vertical section diagram of the rotary compressor according to the embodiment.
- a rotary compressor 40 according to the embodiment is different from the rotary compressor of the described first embodiment in that the rotator 21 is fixed to the crank shaft 16 such that the stator-coil gap shielding ratio is 0% (that is, the upper end face 23a of the rotor core 23 and the upper end face 30a situated at the upside of the stator core 30 are situated on the same plane), and the open ends situated at the exit sides of the communicating channels 35 are closed by a band member (closing member) 41. Since other components are the same as those in the first embodiment, description of them is omitted here.
- the same members as in the first embodiment are marked with the same references respectively.
- the band member 41 is a belt-like (film-like) or wire-like member including a heat-resistant and refrigerant-resistant material (polyester series material), and wind so as to close the open ends situated at the exit sides of the communicating channels 35.
- the band member 41 prevents the mixture, which has flown into the communicating channels 35 through the open ends situated at the entrance sides of the communicating channels 35, from leaking (escaping) into the barrel 2a of the housing 2 through the open ends situated at the exit sides of the communicating channels 35.
- the band member 41 is simply used to close the open ends situated at the exit sides of the communicating channels 35, thereby the amount of mixture leaking (escaping) into the barrel 2a of the housing 2 through the communicating channels 35 can be made zero (or extremely reduced), and the amount of the mixture colliding with the crossover portion 32 can be increased, consequently separation efficiency of oil particles can be improved.
- the refrigerant gas containing oil can be prevented from outflowing into a refrigerant circuit using the rotary compressor 40, consequently system COP of the refrigerant circuit as a whole can be improved.
- the band member 41 was used to close the open ends situated at the exit sides of the communicating channels 35 in the embodiment, the invention is not limited to such a configuration, and a configuration where the band member 41 is used to close the open ends situated at the entrance sides of the communicating channels 35 may be used, or a configuration where the band member 41 is used to close the open ends situated at both of the entrance sides and the exit sides of the communicating channels 35 may be used.
- a third embodiment of the rotary compressor according to the invention is described.
- a rotary compressor according to the embodiment is different from the rotary compressor of the described embodiments in that the rotator 21 is fixed to the crank shaft 16 such that the stator-coil gap shielding ratio is 0% (that is, the upper end face 23a of the rotor core 23 and the upper end face 30a situated at the upside of the stator core 30 are situated on the same plane), and the crossover portion 32 is formed such that the communicating channels 35 are not formed, or each communicating channel 35 is formed such that inner diameter of the communicating channel 35 is smaller than that in each of the described embodiments.
- the amount of the mixture leaking (escaping) into the barrel 2a of the housing 2 through the communicating channels 35 can be zero or extremely reduced (minimized), and the amount of the mixture colliding with the crossover portion 32 can be increased, consequently separation efficiency of oil particles can be improved.
- the refrigerant gas containing oil can be prevented from outflowing into a refrigerant circuit using the rotary compressor, consequently system COP of the refrigerant circuit as a whole can be improved.
- oil can be prevented from outflowing to the outside of the housing 2, so that the lubricant can be avoided from being insufficiently supplied to respective components in the housing 2, consequently life of the rotary compressor can be increased.
- the invention is not limited to the above embodiments, and can be carried out with being appropriately modified or altered within a scope without departing from the gist of the invention.
- the first embodiment and the second embodiment may be carried out in a combined manner, or the first embodiment and the third embodiment may be carried out in a combined manner.
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- Applications Or Details Of Rotary Compressors (AREA)
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Abstract
Description
- The present invention relates to a rotary compressor.
- A rotary compressor is used for compressing a gas refrigerant in a refrigerant circuit in an air conditioning system such as a room air conditioner or a packaged air conditioner.
As such a rotary compressor, for example, a rotary compressor disclosed inpatent document 1 is known.
Patent document 1: Japanese Unexamined Patent Application, Publication No.2005-337210 - In the rotary compressor disclosed in the
patent document 1, a plurality of communicating channels are formed in a proximal end of a crossover portion of a stator core situated in the upside, each of which extends along a direction perpendicular to a rotation axis of a crank shaft, and communicates between the inside of a concave portion formed by the crossover portion of the stator core situated in the upside, and the inside of a barrel of a housing. Therefore, there has been a problem that a part of a mixture of a lubricant and a refrigerant gas, the mixture being introduced into the concave portion through a plurality of passages extending in a vertical direction along an axial hole of a rotor core, is discharged from the rotary compressor through the communicating channels, consequently the part of the mixture outflows into a refrigerant circuit at a downstream side. - The invention was made in the light of the above circumstance, and an object of the invention is to provide a rotary compressor that can improve oil separation efficiency.
- The invention employs the following means for solving the problem.
A first aspect of the rotary compressor according to the invention includes a rotary compressor having a housing, a compression mechanism section accommodated in a lower side of the housing, and a drive part accommodated in an upper side of the housing, in which the drive part has a rotator that is fitly fixed around a crank shaft, and rotates with the crank shaft, and a stator that is disposed at an outer circumferential side of the rotator and fixed to the housing, an oil separator plate is attached to an upper end face of a rotor core of the rotator such that the separator plate covers the upper end face, and is situated in a concave portion formed by a crossover portion projecting from an upper end face of a stator core of the stator, and a plurality of communicating channels, which communicates between the inside of the concave portion and the inside of a barrel of the housing, are formed at a proximal end of the crossover portion; wherein the rotator is fixed to the crank shaft such that the upper end face of the rotor core is situated at a position upper than the upper end face of the stator core, and when an open end situated at an entrance side of a communicating channel is seen from an open end situated at an exit side of the relevant communicating channel, a covering ratio of the open end, which is situated at the entrance side of the communicating channel, by a side face of the rotor core is 30% to 80%. - According to the rotary compressor according to the first aspect, when the open end situated at the entrance side of the communicating channel is seen from the open end situated at the exit side of the same communicating channel, a covering ratio of the open end, which is situated at the entrance side of the communicating channel, by the side face of the rotor core (stator-coil gap shielding ratio) is 30% to 80%, thereby the amount of mixture leaking (escaping) into the barrel of the housing through the communicating channels can be reduced, and the amount of mixture colliding with the crossover portion can be increased, consequently separation efficiency of oil particles can be improved.
Moreover, oil can be prevented from outflowing to the outside of the housing, so that a lubricant can be avoided from being insufficiently supplied to respective components within the housing, consequently life of the rotary compressor can be increased. - A second aspect of the rotary compressor according to the invention includes a rotary compressor having a housing, a compression mechanism section accommodated in a lower side of the housing, and a drive part accommodated in an upper side of the housing, in which the drive part has a rotator that is fitly fixed around a crank shaft, and rotates with the crank shaft, and a stator that is disposed at an outer circumferential side of the rotator and fixed to the housing, an oil separator plate is attached to an upper end face of a rotor core of the rotator such that the oil separator plate covers the upper end face, and is situated in a concave portion formed by a crossover portion projecting from an upper end face of a stator core of the stator, and a plurality of communicating channels, which communicates between the inside of the concave portion and the inside of a barrel of the housing, are formed at a proximal end of the crossover portion; wherein a closing member is provided over entrance ends and/or exit ends of the communicating channels.
- According to the rotary compressor according to the second aspect, the closing member is simply used to close the open ends situated at the exit sides of the communicating channels, thereby the amount of mixture leaking (escaping) into the barrel of the housing through the communicating channels can be made zero (or extremely reduced), and the amount of the mixture colliding with the crossover portion can be increased, consequently separation efficiency of oil particles can be improved.
Moreover, oil can be prevented from outflowing to the outside of the housing, so that a lubricant can be avoided from being insufficiently supplied to respective components within the housing, consequently life of the rotary compressor can be increased. - A third aspect of the rotary compressor according to the invention includes a rotary compressor having a housing, a compression mechanism section accommodated in a lower side of the housing, and a drive part accommodated in an upper side of the housing, in which the drive part has a rotator that is fitly fixed around a crank shaft, and rotates with the crank shaft, and a stator that is disposed at an outer circumferential side of the rotator and fixed to the housing, an oil separator plate is attached to an upper end face of a rotor core of the rotator such that the oil separator covers the upper end face, and is situated in a concave portion formed by a crossover portion projecting from an upper end face of a stator core of the stator, and a plurality of communicating channels, which communicate between the inside of the concave portion and the inside of a barrel of the housing, are formed at a proximal end of the crossover portion; wherein the communicating channels are formed such that the amount of a mixture of oil particles and a refrigerant gas outflowing into the barrel of the housing through the communicating channels is zero or extremely small amount.
- According to the rotary compressor according to the third aspect, the amount of mixture leaking (escaping) into the barrel of the housing through the communicating channels can be zero or extremely reduced (minimized), and the amount of the mixture colliding with the crossover portion can be increased, consequently separation efficiency of oil particles can be improved.
Moreover, oil can be prevented from outflowing to the outside of the housing, so that a lubricant can be avoided from being insufficiently supplied to respective components within the housing, consequently life of the rotary compressor can be increased. - In an air conditioning system according to a fourth aspect of the invention, since a rotary compressor having improved oil separation efficiency is provided, a refrigerant gas containing oil can be prevented from outflowing into a refrigerant circuit, consequently system COP of the refrigerant circuit as a whole can be extremely improved.
- According to the invention, an advantage that oil separation efficiency can be improved is obtained.
-
- [
Fig. 1] Fig. 1 shows a schematic, vertical section diagram of a rotary compressor according to a first embodiment of the invention. - [
Fig. 2] Fig. 2 shows an enlarged vertical section diagram of a relevant part ofFig. 1 . - [
Fig. 3] Fig. 3 shows a graph showing a relationship between compressor efficiency and a stator-coil gap shielding ratio, and a relationship between system COP and the stator-coil gap shielding ratio in the rotary compressor according to the first embodiment of the invention. - [
Fig. 4] Fig. 4 shows a schematic, vertical section diagram of a rotary compressor according to a second embodiment of the invention. -
- 1:
- rotary compressor
- 2:
- housing
- 2a:
- barrel
- 3:
- compression mechanism section
- 4:
- drive part
- 16:
- crank shaft
- 21:
- rotator
- 22:
- stator
- 23:
- rotor core
- 23a:
- upper end face
- 23b:
- side face
- 28:
- oil separator plate
- 30:
- stator core
- 30a:
- upper end face
- 32:
- crossover portion
- 33:
- concave portion
- 35:
- communicating channel
- 40:
- rotary compressor
- 41:
- band member (closing member)
- Hereinafter, a first embodiment of a rotary compressor according to the invention is described according to
Figs. 1 to 3 .
Fig. 1 shows a schematic, vertical section diagram of a rotary compressor according to the embodiment,Fig. 2 shows an enlarged vertical section diagram of a relevant part ofFig. 1 , andFig. 3 shows a graph showing a relationship between compressor efficiency and a stator-coil gap shielding ratio, and a relationship between system COP and the stator-coil gap shielding ratio in the rotary compressor according to the embodiment. - A
rotary compressor 1 according to the embodiment is provided on a refrigerant circuit of an air conditioning system such as a room air conditioner or packaged air conditioner, and used for compressing a gas refrigerant circulating through the refrigerant circuit.
As shown inFig. 1 , therotary compressor 1 has ahousing 2 being a closed vessel, and acompression mechanism section 3 for compressing a gas refrigerant supplied from the refrigerant circuit, and adrive part 4 for driving thecompression mechanism section 3 are accommodated in thehousing 2. - In the embodiment, the
housing 2 is formed as an approximately cylindrical, closed vessel being closed at both ends, and installed with an approximately vertical axis. Thecompression mechanism section 3 is disposed in a lower side of thehousing 2, and thedrive part 4 is disposed above thecompression mechanism section 3.
A lower side-face of thehousing 2 is inserted with refrigerant pipes P1 and P2 of the refrigerant circuit from the outside, and the gas refrigerant is supplied from the refrigerant circuit to thecompression mechanism section 3 through the refrigerant pipes P1 and P2.
Here, while not shown, an oil reservoir room is provided in a bottom of thehousing 2, and a lubricant used for lubrication of thecompression mechanism section 3 and the like is reserved in the oil reservoir room. - The
compression mechanism section 3 compresses the gas refrigerant supplied through the refrigerant pipes P1 and P2 into a high-pressure compressed gas, then sends out the gas into thehousing 2.
Here, a top of thehousing 2 is inserted with a refrigerant pipe P3 from the outside, and the compressed gas being temporarily reserved in thehousing 2 is sent to a downstream side of the refrigerant circuit through the refrigerant pipe P3. - The
compression mechanism section 3 has a plurality ofcylinders 11 each having a cylindrical inner-face 12, and thecylinders 11 are adjacently disposed in an axial direction in a manner that respective cylindrical inner-faces 12 are approximately coaxial with each other, and aseparator 13 is interposed between the cylinders.
Acylindrical rotor 14 having a smaller diameter than that of each cylindrical inner-face 12 is provided within each of thecylinders 11 with its axis being approximately parallel to an axis of each cylindrical inner-face 12. - A
crank shaft 16 is inserted through thecylinders 11,separator 13, androtors 14. Thecrank shaft 16 is provided with its axis being approximately parallel to an array direction of thecylinders 11, and inserted into thecompression mechanism section 3 at a lower-end side. Here, thecrank shaft 16 is supported at an upper-end side by thedrive part 4, and rotationally driven about the axis by thedrive part 4. In the embodiment, thedrive part 4 includes an electromotive motor having a rotor holding the upper-end side of thecrank shaft 16, and the rotor is rotated to rotationally drive thecrank shaft 16. - The
crank shaft 16 has a region to be inserted intorespective cylinders 11, in which approximately cylindrical,eccentric shafts 17 are provided, the shafts being engaged with inner circumferential faces of therotors 14 respectively, and thecrank shaft 16 is rotationally driven about the axis, thereby eachrotor 14 is eccentrically rotated in a manner of rolling on the cylindricalinner surface 12 of eachcylinder 11.
Here, theeccentric shafts 17 are provided while eccentric directions thereof are shifted approximately 180 degrees from each other about the axis of the crank shaft 16 (that is, phases are shifted about 180 degrees from each other about the axis). Thus, when thecrank shaft 16 is rotationally driven, inertia moment produced in oneeccentric shaft 17 and inertia moment produced in the othereccentric shaft 17 are cancelled by each other, so that rotation of thecrank shaft 16 is stabilized.
Moreover, an array of thecylinders 11 is mounted withend bearings 18 at one end side and at the other end side respectively, and thecrank shaft 16 is supported by theend bearings 18 while it can be rotated about the axis. - The
drive part 4 has arotator 21 being fitly fixed around thecrank shaft 16, and astator 22 arranged at an outer circumferential side of therotator 21.
Therotator 21 includes a core (hereinafter, called "rotor core") 23 formed by stacking a plurality of thin materials such as silicon steel sheets formed in a certain shape, and therotor core 23 has a plurality of through-holes (hereinafter, called "passages") 25 extending in a vertical direction along anaxial hole 24 of the rotor core. Each of thepassages 25 has a lower end being an open end, and a mixture of a lubricant, which is for smoothly driving thecompression mechanism section 3 and thedrive part 4, and the refrigerant gas flows into thepassages 25 through the open ends. It is also acceptable that a cylindrical body is fitted in theaxial hole 24 of therotor core 23, and thecrank shaft 16 is pressed into the cylindrical body. - On the other hand, as shown in
Fig. 2 , a disk-likeoil separator plate 28 is mounted on anupper end face 23a of therotor core 23 via anattachment stage 26 and fastening members (for example, bolts and nuts) 27 such that theplate 28 covers theupper end face 23a. In theattachment stage 26, a plurality of through-holes 29 are provided, which penetrate thestage 26 in a thickness direction, and are adjusted to open ends provided at upsides of thepassages 25 respectively. The mixture of the lubricant and the refrigerant gas flowing into thepassages 25 through the open ends provided at the lower side of thepassages 25 outflows to the outside of the rotor core 23 (into a space formed between theupper end face 23a of therotor core 23 and the oil separator plate 28) through the open ends provided at the upsides of thepassages 25 and the through-holes 29 as shown in arrows in full line ofFig. 2 . - As shown in
Fig. 1 , thestator 22 includes a core (hereinafter, called "stator core") 30 formed by stacking a plurality of thin materials such as silicon steel sheets formed in a certain shape, and coil ends (crossover portions) 31 wind on teeth of thestator core 30. In this case,crossover portions 32 of the coil ends 31 project from either of end faces 30a and 30b of thestator core 30, and thus form upper and lowerconcave portions compression mechanism section 3. In theconcave portion 33, theattachment stage 26 and theoil separator plate 28 are accommodated. Thestator core 30 is fixed by pressing in abarrel 2a of the housing 2 (shrinkage fit). - As shown in
Fig. 2 , at a proximal end of the crossover portion 32 (end situated at a side of the stator core 30), a plurality of communicatingchannels 35 are formed, each of which extends in a direction perpendicular to the rotation axis of thecrank shaft 16, and communicates between the inside of theconcave portion 33 and the inside of thebarrel 2a of thehousing 2. - In the embodiment, the
rotator 21 is fixed to thecrank shaft 16 such that anupper end face 23a of therotor core 23 is situated at a position upper than theupper end face 30a situated at an upside of thestator core 30, and when an open end situated at an entrance side (inside in a radial direction) of a communicatingchannel 35 is seen from an open end situated at an exit side (outside in a radial direction) of the same communicatingchannel 35, a covering (closing) ratio of the open end, which is situated at the entrance side of the communicatingchannel 35, by aside face 23b of the rotor core 23 (stator-coil gap shielding ratio) is 30% to 80% (most preferably, about 50%). - In the
rotary compressor 1 configured in this way, the mixture (mixture of the refrigerant gas and the lubricant) rising through thepassage 25 outflows into a space formed between theupper end face 23a of therotor core 23 and theoil separator plate 28. Then, the outflowing mixture is radially scattered (dispersed) to acrossover portion 32 side due to centrifugal force caused by rotation of theoil separator plate 28, and collides with thecrossover portion 32. When the mixture collides with the crossover portion in this way, oil in the mixture adheres on a side face of thecrossover portion 32, so that the oil is separated from the refrigerant gas. The separated oil is returned to the oil reservoir room provided in the lower side of thehousing 2 along thestator 22. On the other hand, the separated refrigerant gas is discharged to the outside of thehousing 2 via the refrigerant pipe P3 provided in a top of thehousing 2. - According to the
rotary compressor 1 according to the embodiment, the stator-coil gap shielding ratio is designed to be 30% to 80%, thereby the amount of mixture leaking (escaping) into thebarrel 2a of thehousing 2 through the communicatingchannel 35 can be reduced, and the amount of mixture colliding with thecrossover portion 32 can be increased, consequently separation efficiency of oil particles can be improved. As a result, as shown inFig. 3 , while compression efficiency is somewhat reduced (because the amount of flux is reduced, and a motor current is increased, thereby motor efficiency is reduced, and magnet pull force is increased, and accordingly thrust loss is increased, leading to increase in mechanical loss), the refrigerant gas containing oil can be prevented from outflowing into a refrigerant circuit using therotary compressor 1, consequently system COP of the refrigerant circuit as a whole can be extremely improved. Moreover, oil can be prevented from outflowing to the outside of thehousing 2, so that the lubricant can be avoided from being insufficiently supplied to respective components in thehousing 2, consequently life of therotary compressor 1 can be increased. - A second embodiment of the rotary compressor according to the invention is described according to
Fig. 4. Fig. 4 shows a schematic, vertical section diagram of the rotary compressor according to the embodiment.
Arotary compressor 40 according to the embodiment is different from the rotary compressor of the described first embodiment in that therotator 21 is fixed to thecrank shaft 16 such that the stator-coil gap shielding ratio is 0% (that is, theupper end face 23a of therotor core 23 and theupper end face 30a situated at the upside of thestator core 30 are situated on the same plane), and the open ends situated at the exit sides of the communicatingchannels 35 are closed by a band member (closing member) 41.
Since other components are the same as those in the first embodiment, description of them is omitted here. InFig. 4 , the same members as in the first embodiment are marked with the same references respectively. - The
band member 41 is a belt-like (film-like) or wire-like member including a heat-resistant and refrigerant-resistant material (polyester series material), and wind so as to close the open ends situated at the exit sides of the communicatingchannels 35. Theband member 41 prevents the mixture, which has flown into the communicatingchannels 35 through the open ends situated at the entrance sides of the communicatingchannels 35, from leaking (escaping) into thebarrel 2a of thehousing 2 through the open ends situated at the exit sides of the communicatingchannels 35. - According to the
rotary compressor 40 according to the embodiment, theband member 41 is simply used to close the open ends situated at the exit sides of the communicatingchannels 35, thereby the amount of mixture leaking (escaping) into thebarrel 2a of thehousing 2 through the communicatingchannels 35 can be made zero (or extremely reduced), and the amount of the mixture colliding with thecrossover portion 32 can be increased, consequently separation efficiency of oil particles can be improved. As a result, the refrigerant gas containing oil can be prevented from outflowing into a refrigerant circuit using therotary compressor 40, consequently system COP of the refrigerant circuit as a whole can be improved. Moreover, oil can be prevented from outflowing to the outside of thehousing 2, so that the lubricant can be avoided from being insufficiently supplied to respective components in thehousing 2, consequently life of therotary compressor 40 can be increased.
While description was made on a configuration where theband member 41 was used to close the open ends situated at the exit sides of the communicatingchannels 35 in the embodiment, the invention is not limited to such a configuration, and a configuration where theband member 41 is used to close the open ends situated at the entrance sides of the communicatingchannels 35 may be used, or a configuration where theband member 41 is used to close the open ends situated at both of the entrance sides and the exit sides of the communicatingchannels 35 may be used. - A third embodiment of the rotary compressor according to the invention is described.
A rotary compressor according to the embodiment is different from the rotary compressor of the described embodiments in that therotator 21 is fixed to thecrank shaft 16 such that the stator-coil gap shielding ratio is 0% (that is, theupper end face 23a of therotor core 23 and theupper end face 30a situated at the upside of thestator core 30 are situated on the same plane), and thecrossover portion 32 is formed such that the communicatingchannels 35 are not formed, or each communicatingchannel 35 is formed such that inner diameter of the communicatingchannel 35 is smaller than that in each of the described embodiments. - According to the rotary compressor according to the embodiment, the amount of the mixture leaking (escaping) into the
barrel 2a of thehousing 2 through the communicatingchannels 35 can be zero or extremely reduced (minimized), and the amount of the mixture colliding with thecrossover portion 32 can be increased, consequently separation efficiency of oil particles can be improved. As a result, the refrigerant gas containing oil can be prevented from outflowing into a refrigerant circuit using the rotary compressor, consequently system COP of the refrigerant circuit as a whole can be improved. Moreover, oil can be prevented from outflowing to the outside of thehousing 2, so that the lubricant can be avoided from being insufficiently supplied to respective components in thehousing 2, consequently life of the rotary compressor can be increased. - The invention is not limited to the above embodiments, and can be carried out with being appropriately modified or altered within a scope without departing from the gist of the invention. For example, the first embodiment and the second embodiment may be carried out in a combined manner, or the first embodiment and the third embodiment may be carried out in a combined manner.
Claims (4)
- A rotary compressor, comprising a housing, a compression mechanism section accommodated in a lower side of the housing, and a drive part accommodated in an upper side of the housing,
in which the drive part has a rotator that is fitly fixed around a crank shaft, and rotates with the crank shaft, and a stator that is disposed at an outer circumferential side of the rotator and fixed to the housing,
an oil separator plate is attached to an upper end face of a rotor core of the rotator such that the oil separator plate covers the upper end face, and is situated in a concave portion formed by a crossover portion projecting from an upper end face of a stator core of the stator, and
a plurality of communicating channels, which communicates between the inside of the concave portion and the inside of a barrel of the housing, are formed at a proximal end of the crossover portion, the rotary compressor being characterized in that:the rotator is fixed to the crank shaft such that the upper end face of the rotor core is situated at a position upper than the upper end face of the stator core, andwhen an open end situated at an entrance side of a communicating channel is seen from an open end situated at an exit side of the relevant communicating channel, a covering ratio of the open end, which is situated at the entrance side of the communicating channel, by a side face of the rotor core is 30% to 80%. - A rotary compressor, comprising a housing, a compression mechanism section accommodated in a lower side of the housing, and a drive part accommodated in an upper side of the housing,
in which the drive part has a rotator that is fitly fixed around a crank shaft, and rotates with the crank shaft, and a stator that is disposed at an outer circumferential side of the rotator and fixed to the housing,
an oil separator plate is attached to an upper end face of a rotor core of the rotator such that the oil separator plate covers the upper end face, and is situated in a concave portion formed by a crossover portion projecting from an upper end face of a stator core of the stator, and
a plurality of communicating channels, which communicate between the inside of the concave portion and the inside of a barrel of the housing, are formed at a proximal end of the crossover portion, the rotary compressor being characterized in that:a closing member is provided over entrance ends and/or exit ends of the communicating channels. - A rotary compressor, comprising a housing, a compression mechanism section accommodated in a lower side of the housing, and a drive part accommodated in an upper side of the housing,
in which the drive part has a rotator that is fitly fixed around a crank shaft, and rotates with the crank shaft, and a stator that is disposed at an outer circumferential side of the rotator and fixed to the housing,
an oil separator plate is attached to an upper end face of a rotor core of the rotator such that the oil separator plate covers the upper end face, and is situated in a concave portion formed by a crossover portion projecting from an upper end face of a stator core of the stator, and
a plurality of communicating channels, which communicate between the inside of the concave portion and the inside of a barrel of the housing, are formed at a proximal end of the crossover portion, the rotary compressor being characterized in that:the communicating channels are formed such that the amount of a mixture of oil particles and a refrigerant gas outflowing into the barrel of the housing through the communicating channels is zero or extremely small amount. - An air conditioning system comprising the rotary compressor according to any one of claims 1 to 3.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007027235A JP5138236B2 (en) | 2007-02-06 | 2007-02-06 | Rotary compressor |
PCT/JP2008/050097 WO2008096560A1 (en) | 2007-02-06 | 2008-01-09 | Rotary compressor |
Publications (3)
Publication Number | Publication Date |
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EP2169232A1 true EP2169232A1 (en) | 2010-03-31 |
EP2169232A4 EP2169232A4 (en) | 2014-08-06 |
EP2169232B1 EP2169232B1 (en) | 2017-03-15 |
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ID=39681471
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP08710540.9A Active EP2169232B1 (en) | 2007-02-06 | 2008-01-09 | Rotary compressor |
Country Status (4)
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EP (1) | EP2169232B1 (en) |
JP (1) | JP5138236B2 (en) |
CN (1) | CN101568731B (en) |
WO (1) | WO2008096560A1 (en) |
Families Citing this family (3)
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CN105090043B (en) * | 2015-09-17 | 2017-06-16 | 广东美芝制冷设备有限公司 | Rotary compressor |
CN106640661B (en) * | 2016-10-26 | 2019-04-05 | 广东美芝制冷设备有限公司 | Rotary compressor and refrigerating plant with it |
CN107917081A (en) * | 2017-11-20 | 2018-04-17 | 珠海格力节能环保制冷技术研究中心有限公司 | Leakproof oil cap, rotor assembly, compressor and air-conditioning system |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60187377U (en) * | 1984-05-24 | 1985-12-12 | 株式会社東芝 | Hermetic electric compressor |
EP1712793A1 (en) * | 2004-02-06 | 2006-10-18 | Daikin Industries, Ltd. | Compressor and method of plate installation |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3418470B2 (en) * | 1994-12-20 | 2003-06-23 | 東芝キヤリア株式会社 | Rotary compressor |
KR20030028376A (en) * | 2001-09-28 | 2003-04-08 | 산요 덴키 가부시키가이샤 | Rotary compressor and method for manufacturing the same |
JP2006336463A (en) * | 2003-09-24 | 2006-12-14 | Matsushita Electric Ind Co Ltd | Compressor |
JP2007518911A (en) * | 2003-09-26 | 2007-07-12 | 松下電器産業株式会社 | Compressor |
JP4365729B2 (en) * | 2004-05-31 | 2009-11-18 | 三菱重工業株式会社 | Rotary compressor |
-
2007
- 2007-02-06 JP JP2007027235A patent/JP5138236B2/en active Active
-
2008
- 2008-01-09 CN CN200880001210.5A patent/CN101568731B/en active Active
- 2008-01-09 WO PCT/JP2008/050097 patent/WO2008096560A1/en active Application Filing
- 2008-01-09 EP EP08710540.9A patent/EP2169232B1/en active Active
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60187377U (en) * | 1984-05-24 | 1985-12-12 | 株式会社東芝 | Hermetic electric compressor |
EP1712793A1 (en) * | 2004-02-06 | 2006-10-18 | Daikin Industries, Ltd. | Compressor and method of plate installation |
Non-Patent Citations (1)
Title |
---|
See also references of WO2008096560A1 * |
Also Published As
Publication number | Publication date |
---|---|
JP2008190466A (en) | 2008-08-21 |
JP5138236B2 (en) | 2013-02-06 |
CN101568731B (en) | 2011-12-28 |
CN101568731A (en) | 2009-10-28 |
WO2008096560A1 (en) | 2008-08-14 |
EP2169232A4 (en) | 2014-08-06 |
EP2169232B1 (en) | 2017-03-15 |
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