EP3239526B1 - Electrically driven scroll compressor - Google Patents
Electrically driven scroll compressor Download PDFInfo
- Publication number
- EP3239526B1 EP3239526B1 EP15872905.3A EP15872905A EP3239526B1 EP 3239526 B1 EP3239526 B1 EP 3239526B1 EP 15872905 A EP15872905 A EP 15872905A EP 3239526 B1 EP3239526 B1 EP 3239526B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- end plate
- housing member
- motor
- orbiting scroll
- accommodation
- 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
Links
- 230000004308 accommodation Effects 0.000 claims description 93
- 230000006835 compression Effects 0.000 claims description 34
- 238000007906 compression Methods 0.000 claims description 34
- 230000002265 prevention Effects 0.000 claims description 14
- 230000008878 coupling Effects 0.000 claims description 10
- 238000010168 coupling process Methods 0.000 claims description 10
- 238000005859 coupling reaction Methods 0.000 claims description 10
- 230000002093 peripheral effect Effects 0.000 description 12
- 239000003507 refrigerant Substances 0.000 description 12
- 230000003014 reinforcing effect Effects 0.000 description 7
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical group [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 5
- 230000000694 effects Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 2
- ZZUFCTLCJUWOSV-UHFFFAOYSA-N furosemide Chemical compound C1=C(Cl)C(S(=O)(=O)N)=CC(C(O)=O)=C1NCC1=CC=CO1 ZZUFCTLCJUWOSV-UHFFFAOYSA-N 0.000 description 2
- 229910052742 iron Inorganic materials 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000003245 working effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
-
- 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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
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- 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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
- F04C29/063—Sound absorbing materials
Definitions
- the present invention relates to an electrically driven scroll compressor used for the refrigerating cycle or the like of a vehicle air conditioning apparatus.
- the known structure of a conventional electrically driven scroll compressor is disclosed in PTL 1.
- the conventional electrically driven scroll compressor includes a discharge housing that has a discharge port and accommodates a compression part (compression mechanism) including a fixed scroll and a movable scroll facing each other, a suction housing provided with a suction port, and an intermediate housing that is present between the discharge housing and the suction housing and accommodates an electric motor together with the suction housing.
- the intermediate housing includes a motor fixing part that accommodates and fixes part of the electric motor and a bearing support part (end plate) that is formed integrally on the discharge housing side of the motor fixing part and supports a driving shaft via a bearing.
- the compression mechanism used in the conventional electrically driven scroll compressor is already known and includes a fixed scroll having a board and a spiral wall erected from the board and an orbiting scroll, disposed facing the fixed scroll, that has a board and a spiral wall erected from the board.
- a rotation prevention mechanism for preventing the rotation of the orbiting scroll is provided.
- this rotation prevention mechanism an Oldham coupling, a pin and ring coupling , a ball coupling, or the like is used between the board (bottom plate) of the orbiting scroll (movable scroll) and the end plate of the intermediate housing.
- the orbiting scroll is revolved so as to be supported by the end plate of the intermediate housing via the rotation prevention mechanism or revolved so as to be supported directly by the end plate of the intermediate
- PTL 2 discloses a scroll compressor having a vibration isolator that is capable of absorbing vibrations generated at movable scroll so as to prevent transfer of vibrations from scroll to the mounting element through outer housing.
- An object of the invention is to provide an electrically driven scroll compressor capable of suppressing the deformation of the end plate, improving the accuracy of the supporting surface for the orbiting scroll, enabling the accurate revolution of the orbiting scroll, and improving the performance and reliability of the compressor.
- the invention relates to an electrically driven scroll compressor 1 including a compression mechanism accommodation housing member 5 for accommodating a compression mechanism 3 that is a combination of a fixed scroll 11 and an orbiting scroll 21, a motor accommodation housing member 6 for accommodating an electric motor 4 for driving the compression mechanism 3, and an inverter accommodation housing member 7 for accommodating an inverter device for driving and controlling the electric motor 4.
- the motor accommodation housing member 6 includes a cylindrical motor fixing part 12 to which a stator 16 of the electric motor 4 is fixed by close-fitting, an end plate 13 having an orbiting scroll side end surface 22, which is a supporting surface for the orbiting scroll 21, and a low rigidity part 14 making connection between the motor fixing part 12 and the end plate 13.
- the low rigidity part 14 has rigidity smaller than in the motor fixing part 12 and the end plate 13.
- the stator of the electric motor when the stator of the electric motor is fixed to the motor fixing part of the motor accommodation housing member by close-fitting and the motor fixing part undergoes diameter expansion deformation by the stator, the low rigidity part having rigidity smaller than in the motor fixing part and the end plate is elastically deformed by the diameter expansion deformation of the motor fixing part, the diameter expansion deformation of the motor fixing part is absorbed by the low rigidity part, and the stress caused in the connection part between the low rigidity part and the end plate becomes smaller than in the case in which the low rigidity part is not provided.
- the orbiting scroll can revolve at high accuracy and the performance and reliability of the compressor can be improved.
- the electrically driven scroll compressor 1 illustrated in Fig. 1 is an electrically driven compressor suitable for a refrigerating cycle that uses a refrigerant as a working fluid.
- the compression mechanism 3 is disposed on the right side in the drawing of a housing 2 made of aluminum alloy
- the electric motor 4 for driving the compression mechanism 3 is disposed in the middle of the housing 2
- an inverter device (not illustrated) is disposed on the left side of the housing 2.
- the left side in the drawing is the front of the compressor and the right side is the rear of the compressor.
- the housing 2 includes the compression mechanism accommodation housing member 5 in which the compression mechanism 3 is accommodated, the motor accommodation housing member 6 in which the electric motor 4 for driving the compression mechanism 3 is accommodated, and the inverter accommodation housing member 7 in which the inverter device (not illustrated) for driving and controlling the electric motor 4 is accommodated.
- the compression mechanism accommodation housing member 5 and the motor accommodation housing member 6 adjacent to each other are positioned by a positioning pin (not illustrated) and fixed in the shaft direction (X-axis direction in Fig. 1 ) by a tightening bolt 8.
- the motor accommodation housing member 6 and the inverter accommodation housing member 7 adjacent to each other are positioned by a positioning pin (not illustrated) and fixed in the shaft direction by a tightening bolt 10.
- the compression mechanism housing member 5 accommodates the fixed scroll 11 of the compression mechanism 3, which will be described later, and is formed in a bottomed cylinder having an opening at the end facing the motor accommodation housing member 6.
- the motor accommodation housing member 6 includes the cylindrical motor fixing part 12 to which the electric motor 4 is fixed, the end plate 13 positioned on the side facing the compression mechanism accommodation housing member 5, and the low rigidity part 14 that is positioned between the motor fixing part 12 and the end plate 13 and makes connection between one end side in the shaft direction of the motor fixing part 12 and the radially outer end side of the end plate 13.
- the motor fixing part 12, the low rigidity part 14, and the end plate 13 are formed integrally with each other and the low rigidity part 14 has rigidity smaller than in the motor fixing part 12 and the end plate 13.
- the low rigidity part 14 is formed across the entire circumference in the circumferential direction of the motor accommodation housing member 6 and has a constriction part 15 formed by recessing a part between the motor fixing part 12 and the end plate 13 radially inward.
- the low rigidity part 14 is elastically deformed by the diameter expansion deformation of the motor fixing part 12, absorbs the deformation of the motor fixing part 12, and suppresses the deformation of the end plate 13 caused by the diameter expansion deformation of the motor fixing part 12.
- bolt accommodation parts 17 are formed on the low rigidity part 14 so as to project radially outward as described later.
- the constriction part 15 is recessed radially inward so that a recession amount d equals approximately 0.05D from the outer surface of the motor fixing part 12.
- the wall thickness of the low rigidity part 14 is assumed to be t
- the constriction part 15 is recessed radially inward so that the recession amount d of the motor fixing part 12 from the outer surface of the motor fixing part 12 equals t/2 or more.
- the amount of recession of the constriction part 15 is not limited to this amount of recession illustrated above and the optimum amount of recession is determined in consideration of the amount of diameter expansion deformation of the motor fixing part 12 and the like.
- the end plate 13 is formed integrally with a shaft supporting part 20 supporting one end side of a driving shaft 18 so that the orbiting scroll side end surface 22 can support loads in the shaft direction of the orbiting scroll 21 of the compression mechanism 3.
- the inverter accommodation housing member 7 includes an inverter accommodation cylindrical part 23 formed in a cylindrical shape and an end plate 24, formed integrally with the inverter accommodation cylindrical part 23, that is positioned on the side facing the motor accommodation housing member 6.
- the end plate 24 is formed integrally with a shaft supporting part 25 for supporting the other end side of the driving shaft 18.
- the shaft supporting part 20 of the end plate 13 of the motor accommodation housing member 6 rotatably supports one end side of the driving shaft 18 via a bearing 26.
- the shaft supporting part 25 of the end plate 24 of the inverter accommodation housing member 7 rotatably supports the other end side of the driving shaft 18 via a bearing 27.
- the interior of the housing 2 is partitioned by the end plate 13 of the motor accommodation housing member 6 and the end plate 24 of the inverter accommodation housing member 7 into a compression mechanism accommodation part 28 in which the compression mechanism 3 is accommodated, a motor accommodation part 30 in which the electric motor 4 is accommodated, and an inverter accommodation part 31 in which the inverter device is accommodated, in sequence from the rear side.
- the inverter accommodation part 31 is closed by fixing a lid 32 to the opening of the inverter accommodation housing member 7 by a bolt (not illustrated) or the like.
- the compression mechanism 3 is a scroll type mechanism having the fixed scroll 11 and the orbiting scroll 21 disposed facing the fixed scroll 11.
- the fixed scroll 11 is allowed to move in the shaft direction and prevented from moving in the radial direction by positioning pins 33, which will be described later, with respect to the housing 2 (compression mechanism accommodation housing member 5).
- the fixed scroll 11 includes a discoid board 11a, a cylindrical outer peripheral wall 11b, provided across the entire circumference along the outer edge of the board 11a, that is erected toward the front, and a spiral wall 11c extending toward the front from the board 11a in the outer peripheral wall 11b.
- the orbiting scroll 21 includes a discoid board 21a and a spiral wall 21c erected backward from the board 21a.
- a radial bearing 35 is accommodated in an engagement concave portion 34 provided at the center of the back of the board 21a and the orbiting scroll 21 is supported by an eccentric shaft 36 formed in the rear end section of the driving shaft 18 via the radial bearing 35.
- the orbiting scroll 21 can perform revolving motion about the shaft center of the driving shaft 18 according to the eccentric amount between the shaft center of the driving shaft 18 and the shaft center of the eccentric shaft 36.
- the spiral wall 11c of the fixed scroll 11 is engaged with the spiral wall 21c of the orbiting scroll 21 and a compression chamber 37 is formed by the space surrounded by the board 11a and the spiral wall 11c of the fixed scroll 11 and the board 21a and the spiral wall 21c of the orbiting scroll 21.
- the fixed scroll 11 and the end plate 13 of the motor accommodation housing member 6 are radially positioned by the positioning pins 33.
- the invention is not limited to the embodiment and an annular thrust race (not illustrated) like a thin plate may be present between the outer peripheral wall 11b of the fixed scroll 11 and the end plate 13 so that the fixed scroll 11 faces the end plate 13 via the thrust race and the loads in the shaft direction of the orbiting scroll 21 are supported by the end plate 13 via the thrust race.
- the shaft supporting part 20 formed integrally with the end plate 13 of the motor accommodation housing member 6 is provided with a weight accommodation part 38, which is an annular concave part opened toward the compressor accommodation part 28, a bearing accommodation part 40, which is an annular concave part opened toward the motor accommodation part 30, and a through hole 41 penetrating through the weight accommodation part 38 and the bearing accommodation part 40 along the driving shaft 18.
- the weight accommodation part 38 accommodates a balance weight 42 rotating integrally with the driving shaft 18.
- the bearing accommodation part 40 accommodates the bearing 26 rotatably supporting one end side of the driving shaft 18.
- the through hole 41 accommodates the driving shaft 18 with a sufficient clearance left.
- a discharge chamber 47 is formed between the fixed scroll 11 and a rear end wall 46 of the compression mechanism accommodation housing member 5 in the rear of the fixed scroll 11 in the housing 2.
- the refrigerant gas compressed by the compression chamber 37 is discharged to this discharge chamber 47 via a discharge hole 48 formed substantially at the center of the fixed scroll 11.
- the refrigerant gas having been discharged to the discharge chamber 47 is press-fed to an external refrigerant circuit via a discharge opening 50.
- the motor fixing part 12 which is formed ahead of the end plate 13 of the motor accommodation housing member 6, accommodates the stator 16 and a rotor 51 constituting the electric motor 4.
- the stator 16 includes a cylindrical iron core and a coil wound therearound and the stator 16 is fixed to the inner surface of the housing 2 (motor accommodation housing member 6).
- the rotor 51 including a magnet is fixed to the outer peripheral side of the driving shaft 18 and rotatably accommodated within the stator 16. The rotor 51 is rotated integrally with the driving shaft 18 by a rotary magnetic force generated by the stator 16.
- the inverter device to be accommodated in the inverter accommodation housing member 7 is electrically connected to the stator 16 via a terminal (airtight terminal) attached to a through hole (not illustrated) formed in the end plate 24 and supplies electricity to the electric motor 4.
- the suction opening 43 through which refrigerant gas is sucked to the motor accommodation part 30 is formed in the side surface of the housing 2 (motor accommodation housing member 6).
- the refrigerant having flowed into the motor accommodation part 30 through the suction opening 43 is introduced to the suction chamber 45 via the suction route 44.
- the suction route 44 includes the clearance between the stator 16 and the housing 2 (motor accommodation housing member 6), holes 52 formed in the end plate 13, the clearance formed between the fixed scroll 11 and the housing 2, and the like.
- stator contact parts 53 in contact with the stator 16 and stator non-contact parts 54 not in contact with the stator 16 are alternately formed in the circumferential direction.
- the outer peripheral part of the stator 16 is fixed to the stator contact parts 53 by close-fitting (such as press-fitting or shrink-fitting). This fixes the stator 16 to the housing 2 (motor accommodation housing member 6).
- the clearance between the stator 16 and the housing 2 (motor accommodation housing member 6) that configures part of the suction route 44 is formed by the clearance between the inner walls of the stator non-contact parts 54 and the outer peripheral part of the stator 16.
- stator contact part 53 and the stator non-contact part 54 are formed in the circumferential direction at intervals of 60 degrees.
- the length in the circumferential direction of the stator contact part 53 is relatively smaller than the length in the circumferential direction of the stator non-contact part 54 (the length of the stator contact part 53 has a center angle of approximately 20 degrees and the length of the stator non-contact part 54 has a center angle of approximately 40 degrees).
- end plate 13 of the motor accommodation housing member 6 is provided with the holes 52 communicating the motor accommodation part 30 with the compression mechanism accommodation part 28.
- the refrigerant having flowed through the suction opening 43 into the motor accommodation part 30 is introduced to the suction chamber 45 through the holes 52.
- the holes 52 are formed in the end plate 13 so as to be positioned radially outward of pins 55 of a rotation prevention mechanism, which will be described later.
- the plurality of holes 52 are formed in positions radially inward of five stator contact parts 53 and substantially aligned with the five stator contact parts 53 in the circumferential direction (positions having substantially the same phase) so as to correspond to the five stator contact parts 53.
- the holes 52 correspond to only the five stator contact parts 53 of the six stator contact parts 53 and are formed as long holes extending in the circumferential direction of the end plate 13.
- a bolt hole 56 through which a shaft part 10a of the tightening bolt 10 passes is formed between the stator contact parts 53 and 53 adjacent to each other of the end plate 13.
- the tightening bolts 10 having the shaft parts 10a passing through the bolt holes 56 are used to fix the motor accommodation housing member 6 and the inverter accommodation housing member 7.
- the shaft parts 10a of the tightening bolts 10 are fitted to the bolt accommodation parts 17 formed partially in the low rigidity part 14 with a clearance left.
- the bolt accommodation parts 17 are formed in the parts of the low rigidity part 14 into which the shaft parts 10a of the tightening bolts 10 are inserted.
- the bolt accommodation parts 17 project radially outward of the constriction part 15 of the low rigidity part 14, cover the shaft parts 10a of the tightening bolts 10 so that the shaft parts 10a of the tightening bolts 10 are not exposed to outside air, and protect the shaft parts 10a of the tightening bolts 10.
- As many bolt accommodation parts 17 as the tightening bolts 10 are formed and have a substantially circular cross section to improve the rigidity in the twist direction of the low rigidity part 14.
- the surface of the end plate 13 close to the motor accommodation part 30 is provided integrally with reinforcing ribs 57 for reinforcing the end plate 13 extending from the shaft supporting part 20 to the inner peripheral surface of the low rigidity part 14 in the radial direction.
- the plurality of reinforcing ribs 57 are formed at substantially regular intervals in the circumferential direction in positions corresponding to the stator non-contact parts 54 in the shaft direction, that is, in the positions substantially aligned with the stator non-contact parts 54 in the circumferential direction (in the positions having substantially the same phase) (six reinforcing ribs 57 are provided in the circumferential direction so as to correspond to the number of the pins 55, which will be described later) .
- the reinforcing ribs 57 are formed so that their positions in the circumferential direction are not aligned with the stator contact parts 53 (so that they do not have the same phase) to prevent the direct transfer of the stress generated by the deformation of the stator contact parts 53.
- the positioning pins 33 for positioning the fixed scroll 11 with respect to the end plate 13 are provided on a virtual circle 58 including the holes 52 and are fixed by being press-fitted into pin mounting holes 60 formed in the end plate 13.
- the compression chamber 37 of the compression mechanism 3 is moved from the outer peripheral sides of the spiral wall 11c of the fixed scroll 11 and the spiral wall 21c of the orbiting scroll 21 toward the center while gradually reducing its volume by the revolving motion of the orbiting scroll 21.
- the refrigerant gas sucked to the compression chamber 37 from the suction chamber 45 is compressed as the orbiting scroll 21 revolves.
- the compressed refrigerant gas is discharged to the discharge chamber 47 via the discharge hole 48 formed in the board 11a of the fixed scroll 11 and fed to an external refrigerant circuit through the discharge chamber 47 via the discharge opening 50.
- the electrically driven scroll compressor 1 Since a rotation force is generated in the orbiting scroll 21 as the driving shaft 18 rotates in the electrically driven scroll compressor 1 described above, the orbiting scroll 21 needs to be revolved about the shaft center of the driving shaft 18 in the state in which the rotation of the orbiting scroll 21 is restricted. Therefore, the electrically driven scroll compressor 1 according to the embodiment is provided with a rotation prevention mechanism for engaging the pins 55 between the board 21a of the orbiting scroll 21 and the end plate 13 of the motor accommodation housing member 6.
- a pin and ring coupling is adopted as the rotation prevention mechanism and this coupling includes a plurality of the pins 55 disposed in the circumferential direction, a plurality of ring members 61 engaged onto the pins 55, and a plurality of cylindrical concave portions 62 accommodating the ring members 61.
- the cylindrical concave portions 62 are depressions having a circular cross section formed in the back surface (surface facing the end plate 13) of the board 21a of the orbiting scroll 21 and formed at regular intervals (intervals of 60 degrees in this example) around the periphery of the engagement concave portion 34 of the orbiting scroll 21.
- the ring members 61 are annular components made of iron, have an outer diameter smaller than the inner diameter of the cylindrical concave portions 62, and loosely engaged to the cylindrical concave portions 62.
- the length in the shaft direction of the ring members 61 is substantially identical to or smaller than the length in the shaft direction of the cylindrical concave portions 62.
- the pins 55 are formed in cylinders made of iron, have an outer diameter smaller than the inner diameter of the ring members 61, and are fixed at regular intervals to the orbiting scroll side end surface 22 facing the orbiting scroll 21 around the weight accommodation part 38 of the end plate 13 of the motor accommodation housing member 6 so as to be aligned with the positions of the cylindrical concave portions 62.
- the pins 55 are fixed by being press-fitted to pin mount holes 63 formed in the end plate 13 and fixed to the back surface of the part of the end plate 13 in which the reinforcing ribs 57 are formed.
- the motion of the orbiting scroll 21 is restricted because the pins 55 fixed to the end plate 13 make contact with the inner peripheral surfaces of the ring members 61 in the cylindrical concave portions 62 and the pins 55 are engaged to the cylindrical concave portions 62 via the ring members 61.
- the orbiting scroll 21 is allowed only to revolve about the shaft center of the driving shaft 18 in the state in which rotation is restricted.
- the stator 16 of the electric motor 4 when the stator 16 of the electric motor 4 is fixed to the motor fixing part 12 of the motor accommodation housing member 6 by close-fitting and the motor fixing part 12 undergoes diameter expansion deformation by the stator 16, the low rigidity part 14 having rigidity smaller than in the motor fixing part 12 and the end plate 13 is elastically deformed by the diameter expansion deformation of the motor fixing part 12, the diameter expansion deformation of the motor fixing part 12 is absorbed by the low rigidity part 14, and the stress (stress caused by the diameter expansion deformation of the motor fixing part 12) caused in the connection part between the low rigidity part 14 and the end plate 13 becomes smaller than in the case in which the low rigidity part 14 is not provided.
- the orbiting scroll 21 can be revolved at high accuracy and the performance and reliability of the compressor can be improved.
- the low rigidity part 14 is formed across the entire circumference in the circumferential direction of the motor accommodation housing member 6, the diameter expansion deformation of the motor fixing part 12 can be evenly absorbed across the entire circumference in the circumferential direction of the motor accommodation housing member 6 and an imbalanced stress is not generated in the circumferential direction of the end plate 13.
- the low rigidity part 14 since the low rigidity part 14 has the constriction part 15 formed by recessing the part between the motor fixing part 12 and the end plate 13 radially inward, the length of the low rigidity part 14 in the cross sectional view in Fig. 1 is longer than the case in which the constriction part 15 is not provided and the low rigidity part 14 is easily deformed following the diameter expansion deformation of the motor fixing part 12.
- the electrically driven scroll compressor 1 can reduce the stress generated in the connection part between the low rigidity part 14 and the end plate 13, further reducing the deformation of the end plate 13 caused by the diameter expansion deformation of the motor fixing part 12.
- the bolt accommodation parts 17 projecting radially outward are formed partially on the constriction part 15 of the low rigidity part 14, cover the shaft parts 10a of the tightening bolts 10 for fixing the motor accommodation housing member 6 and the inverter accommodation housing member 7 with the bolt accommodation parts 17 so that the shaft parts 10a of the tightening bolts 10 are not exposed to outside air, and protect the shaft parts 10a of the tightening bolts 10 using the bolt accommodation parts 17. Accordingly, reduction in durability caused by corrosion or the like of the tightening bolts 10 can be prevented and the rigidity in the twist direction of the low rigidity part 14 of the motor accommodation housing member 6 can be improved.
- the weight of the orbiting scroll 21 as a movable member can be reduced and the drivability of the orbiting scroll 21 can be improved.
- the pins 55 are press-fitted and fixed to the end plate 13 of the motor accommodation housing member 6, which is a fixing member having rigidity higher than the board 21a of the orbiting scroll 21.
- the end plate 13 hardly deforms when the pins 55 are press-fitted and, even when the pins 55 are engaged to the cylindrical concave portions 62 via the ring members 61 and the pins 55 receive loads in the radial direction, the parts to which the pins 55 are press-fitted are not deformed by the loads in the radial direction, thereby enabling the improvement of the assembly accuracy of the pins 55 (the pins 55 can be prevented from being slanted) . Accordingly, in the electrically driven scroll compressor 1 according to the embodiment, combined with the effects of improving the accuracy of the supporting surface for the end plate 13 described above, the orbiting scroll 21 can be revolved at high accuracy and the performance and reliability of the compressor can be further improved.
- the pins 55 are fixed to the parts of the end plate 13 in which the reinforcing ribs 57 are formed. That is, since the pins 55 are fixed to the parts of the end plate 13 having high rigidity, it is possible to surely prevent the parts to which the pins 55 are press-fitted from being deformed when the pins 55 are press-fitted and fixed or loads in the radial direction are received.
- the electrically driven scroll compressor 1 since the positioning pins 33 for positioning the end plate 13 and the fixed scroll 11 are provided in the positions (on the virtual circle 58 including the plurality of the holes 52) radially outward of the shaft center and the positioning pins 33 are fixed to the end plate 13 prevented from being deformed by the function of the low rigidity part 14, the fixed scroll 11 is positioned on the end plate 13 at high accuracy.
- the electrically driven scroll compressor 1 according to the embodiment can combine the fixed scroll 11 with the orbiting scroll 21 at high accuracy and, combined with various effects of the above embodiment, the performance and reliability of the compressor can be further improved.
- the ring members 61 may be omitted to obtain the rotation prevention function.
- the cylindrical concave portions 62 may be directly engaged onto the pins 55.
- the electrically driven scroll compressor modified to have such a structure can obtain the same working effect as in the electrically driven scroll compressor 1 according to the embodiment.
- the pins 55 of the rotation prevention mechanism are fixed to the end plate 13 and the cylindrical concave portions 62 of the rotation prevention mechanism are formed in the orbiting scroll 21 in the electrically driven scroll compressor 1 according to the embodiment, the invention is not limited to the embodiment and the pins 55 may be fixed to the orbiting scroll 21 and the cylindrical concave portions 62 may be formed in the end plate 13.
- a pin and ring coupling is used as the rotation prevention mechanism in the electrically driven scroll compressor 1 according to the embodiment, the rotation prevention mechanism other than a pin and ring coupling may be used.
Description
- The present invention relates to an electrically driven scroll compressor used for the refrigerating cycle or the like of a vehicle air conditioning apparatus.
- The known structure of a conventional electrically driven scroll compressor is disclosed in PTL 1. The conventional electrically driven scroll compressor includes a discharge housing that has a discharge port and accommodates a compression part (compression mechanism) including a fixed scroll and a movable scroll facing each other, a suction housing provided with a suction port, and an intermediate housing that is present between the discharge housing and the suction housing and accommodates an electric motor together with the suction housing. The intermediate housing includes a motor fixing part that accommodates and fixes part of the electric motor and a bearing support part (end plate) that is formed integrally on the discharge housing side of the motor fixing part and supports a driving shaft via a bearing.
- The compression mechanism used in the conventional electrically driven scroll compressor is already known and includes a fixed scroll having a board and a spiral wall erected from the board and an orbiting scroll, disposed facing the fixed scroll, that has a board and a spiral wall erected from the board. By combining the spiral walls of the pair of scrolls with each other and the orbiting scroll is engaged with and revolved (revolving motion) by the eccentric shaft provided on the driving shaft rotated and driven by the electric motor accommodated in the housing, and the compression chamber formed between the spiral walls of both scrolls is moved toward the center while being reduced in volume to compress the compressed fluid.
- In such an electrically driven scroll compressor, since a rotation force is generated in the orbiting scroll as the driving shaft rotates, a rotation prevention mechanism for preventing the rotation of the orbiting scroll is provided. As this rotation prevention mechanism, an Oldham coupling, a pin and ring coupling , a ball coupling, or the like is used between the board (bottom plate) of the orbiting scroll (movable scroll) and the end plate of the intermediate housing. The orbiting scroll is revolved so as to be supported by the end plate of the intermediate housing via the rotation prevention mechanism or revolved so as to be supported directly by the end plate of the intermediate
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PTL 2 discloses a scroll compressor having a vibration isolator that is capable of absorbing vibrations generated at movable scroll so as to prevent transfer of vibrations from scroll to the mounting element through outer housing. -
- PTL 1:
JP-A-2000-291557 - PTL 2:
EP 2 500 517 A2 - In an electrically driven scroll compressor in which an electric motor is fixed within an intermediate housing by close-fitting of electrically driven scroll compressors having been generally known conventionally, when the electric motor is fixed within the intermediate housing via close-fitting, the intermediate housing undergoes diameter expansion deformation by the electric motor, the diameter expansion deformation of the intermediate housing deforms the end plate of the intermediate housing supporting an orbiting scroll, the accuracy of the supporting surface for the orbiting scroll is reduced, the revolution accuracy of the orbiting scroll is reduced or the smooth revolving motion of the orbiting scroll becomes difficult, possibly affecting the performance and reliability of the compressor.
- An object of the invention is to provide an electrically driven scroll compressor capable of suppressing the deformation of the end plate, improving the accuracy of the supporting surface for the orbiting scroll, enabling the accurate revolution of the orbiting scroll, and improving the performance and reliability of the compressor.
- The invention relates to an electrically driven scroll compressor 1 including a compression mechanism
accommodation housing member 5 for accommodating acompression mechanism 3 that is a combination of afixed scroll 11 and anorbiting scroll 21, a motoraccommodation housing member 6 for accommodating anelectric motor 4 for driving thecompression mechanism 3, and an inverteraccommodation housing member 7 for accommodating an inverter device for driving and controlling theelectric motor 4. In the invention, the motoraccommodation housing member 6 includes a cylindricalmotor fixing part 12 to which astator 16 of theelectric motor 4 is fixed by close-fitting, anend plate 13 having an orbiting scrollside end surface 22, which is a supporting surface for the orbitingscroll 21, and alow rigidity part 14 making connection between themotor fixing part 12 and theend plate 13. In addition, thelow rigidity part 14 has rigidity smaller than in themotor fixing part 12 and theend plate 13. - In the electrically driven scroll compressor according to the invention, when the stator of the electric motor is fixed to the motor fixing part of the motor accommodation housing member by close-fitting and the motor fixing part undergoes diameter expansion deformation by the stator, the low rigidity part having rigidity smaller than in the motor fixing part and the end plate is elastically deformed by the diameter expansion deformation of the motor fixing part, the diameter expansion deformation of the motor fixing part is absorbed by the low rigidity part, and the stress caused in the connection part between the low rigidity part and the end plate becomes smaller than in the case in which the low rigidity part is not provided. As a result, in the electrically driven scroll compressor according to the invention, since the deformation of the end plate caused by the diameter expansion deformation of the motor fixing part can be suppressed and the accuracy of the supporting surface supporting the revolving motion of the orbiting scroll can be improved, the orbiting scroll can revolve at high accuracy and the performance and reliability of the compressor can be improved.
-
-
Fig. 1 is a cross sectional view illustrating the electrically driven scroll compressor according to the invention. -
Fig. 2A is a back view illustrating the orbiting scroll. -
Fig. 2B is a cross sectional view illustrating the orbiting scroll taken along line A1-A1 inFig. 2A . -
Fig. 3A illustrates the motor accommodation housing member with which the end plate is integrated, and the end plate seen in the shaft direction from the motor fixing part. -
Fig. 3B illustrates the end plate in the shaft direction from the compressor mechanism. -
Fig. 4 is a cross sectional view illustrating the motor accommodation housing member taken along line A2-A2 inFig. 1 . - The electrically driven scroll compressor according to the invention will be described below with reference to the drawings.
- The electrically driven scroll compressor 1 illustrated in
Fig. 1 is an electrically driven compressor suitable for a refrigerating cycle that uses a refrigerant as a working fluid. InFig. 1 , thecompression mechanism 3 is disposed on the right side in the drawing of ahousing 2 made of aluminum alloy, theelectric motor 4 for driving thecompression mechanism 3 is disposed in the middle of thehousing 2, and an inverter device (not illustrated) is disposed on the left side of thehousing 2. InFig. 1 , the left side in the drawing is the front of the compressor and the right side is the rear of the compressor. - The
housing 2 includes the compression mechanismaccommodation housing member 5 in which thecompression mechanism 3 is accommodated, the motoraccommodation housing member 6 in which theelectric motor 4 for driving thecompression mechanism 3 is accommodated, and the inverteraccommodation housing member 7 in which the inverter device (not illustrated) for driving and controlling theelectric motor 4 is accommodated. The compression mechanismaccommodation housing member 5 and the motoraccommodation housing member 6 adjacent to each other are positioned by a positioning pin (not illustrated) and fixed in the shaft direction (X-axis direction inFig. 1 ) by a tighteningbolt 8. In addition, the motoraccommodation housing member 6 and the inverteraccommodation housing member 7 adjacent to each other are positioned by a positioning pin (not illustrated) and fixed in the shaft direction by a tightening bolt 10. - The compression
mechanism housing member 5 accommodates thefixed scroll 11 of thecompression mechanism 3, which will be described later, and is formed in a bottomed cylinder having an opening at the end facing the motoraccommodation housing member 6. - The motor
accommodation housing member 6 includes the cylindricalmotor fixing part 12 to which theelectric motor 4 is fixed, theend plate 13 positioned on the side facing the compression mechanismaccommodation housing member 5, and thelow rigidity part 14 that is positioned between themotor fixing part 12 and theend plate 13 and makes connection between one end side in the shaft direction of themotor fixing part 12 and the radially outer end side of theend plate 13. Themotor fixing part 12, thelow rigidity part 14, and theend plate 13 are formed integrally with each other and thelow rigidity part 14 has rigidity smaller than in themotor fixing part 12 and theend plate 13. - The
low rigidity part 14 is formed across the entire circumference in the circumferential direction of the motoraccommodation housing member 6 and has aconstriction part 15 formed by recessing a part between themotor fixing part 12 and theend plate 13 radially inward. As described later, when thestator 16 of theelectric motor 4 is fixed to themotor fixing part 12 by close-fitting (such as press-fitting or shrink-fitting) and themotor fixing part 12 undergoes diameter expansion deformation, thelow rigidity part 14 is elastically deformed by the diameter expansion deformation of themotor fixing part 12, absorbs the deformation of themotor fixing part 12, and suppresses the deformation of theend plate 13 caused by the diameter expansion deformation of themotor fixing part 12. In addition,bolt accommodation parts 17 are formed on thelow rigidity part 14 so as to project radially outward as described later. In the embodiment, when the diameter of themotor fixing part 12 is assumed to be D, theconstriction part 15 is recessed radially inward so that a recession amount d equals approximately 0.05D from the outer surface of themotor fixing part 12. Alternatively, when the wall thickness of thelow rigidity part 14 is assumed to be t, theconstriction part 15 is recessed radially inward so that the recession amount d of themotor fixing part 12 from the outer surface of themotor fixing part 12 equals t/2 or more. However, the amount of recession of theconstriction part 15 is not limited to this amount of recession illustrated above and the optimum amount of recession is determined in consideration of the amount of diameter expansion deformation of themotor fixing part 12 and the like. - The
end plate 13 is formed integrally with ashaft supporting part 20 supporting one end side of adriving shaft 18 so that the orbiting scrollside end surface 22 can support loads in the shaft direction of theorbiting scroll 21 of thecompression mechanism 3. - The inverter
accommodation housing member 7 includes an inverter accommodationcylindrical part 23 formed in a cylindrical shape and anend plate 24, formed integrally with the inverter accommodationcylindrical part 23, that is positioned on the side facing the motoraccommodation housing member 6. Theend plate 24 is formed integrally with ashaft supporting part 25 for supporting the other end side of thedriving shaft 18. - The
shaft supporting part 20 of theend plate 13 of the motoraccommodation housing member 6 rotatably supports one end side of the drivingshaft 18 via abearing 26. In addition, theshaft supporting part 25 of theend plate 24 of the inverteraccommodation housing member 7 rotatably supports the other end side of the drivingshaft 18 via abearing 27. The interior of thehousing 2 is partitioned by theend plate 13 of the motoraccommodation housing member 6 and theend plate 24 of the inverteraccommodation housing member 7 into a compressionmechanism accommodation part 28 in which thecompression mechanism 3 is accommodated, amotor accommodation part 30 in which theelectric motor 4 is accommodated, and aninverter accommodation part 31 in which the inverter device is accommodated, in sequence from the rear side. In this example, theinverter accommodation part 31 is closed by fixing alid 32 to the opening of the inverteraccommodation housing member 7 by a bolt (not illustrated) or the like. - The
compression mechanism 3 is a scroll type mechanism having thefixed scroll 11 and theorbiting scroll 21 disposed facing thefixed scroll 11. Thefixed scroll 11 is allowed to move in the shaft direction and prevented from moving in the radial direction by positioningpins 33, which will be described later, with respect to the housing 2 (compression mechanism accommodation housing member 5). Thefixed scroll 11 includes a discoid board 11a, a cylindrical outerperipheral wall 11b, provided across the entire circumference along the outer edge of the board 11a, that is erected toward the front, and aspiral wall 11c extending toward the front from the board 11a in the outerperipheral wall 11b. - In addition, as illustrated in
Figs. 1 and2 , theorbiting scroll 21 includes adiscoid board 21a and aspiral wall 21c erected backward from theboard 21a. Aradial bearing 35 is accommodated in an engagementconcave portion 34 provided at the center of the back of theboard 21a and the orbitingscroll 21 is supported by aneccentric shaft 36 formed in the rear end section of the drivingshaft 18 via theradial bearing 35. As a result, the orbitingscroll 21 can perform revolving motion about the shaft center of the drivingshaft 18 according to the eccentric amount between the shaft center of the drivingshaft 18 and the shaft center of theeccentric shaft 36. - The
spiral wall 11c of the fixedscroll 11 is engaged with thespiral wall 21c of the orbitingscroll 21 and acompression chamber 37 is formed by the space surrounded by the board 11a and thespiral wall 11c of the fixedscroll 11 and theboard 21a and thespiral wall 21c of the orbitingscroll 21. In addition, the fixedscroll 11 and theend plate 13 of the motoraccommodation housing member 6 are radially positioned by the positioning pins 33. - Although the fixed
scroll 11 is directly assembled to theend plate 13 of the motoraccommodation housing member 6 and the loads in the shaft direction of the orbitingscroll 21 are directly supported by the orbiting scrollside end surface 22 of theend plate 13 in the electrically driven scroll compressor 1 according to the embodiment, the invention is not limited to the embodiment and an annular thrust race (not illustrated) like a thin plate may be present between the outerperipheral wall 11b of the fixedscroll 11 and theend plate 13 so that the fixedscroll 11 faces theend plate 13 via the thrust race and the loads in the shaft direction of the orbitingscroll 21 are supported by theend plate 13 via the thrust race. - The
shaft supporting part 20 formed integrally with theend plate 13 of the motoraccommodation housing member 6 is provided with aweight accommodation part 38, which is an annular concave part opened toward thecompressor accommodation part 28, a bearingaccommodation part 40, which is an annular concave part opened toward themotor accommodation part 30, and a throughhole 41 penetrating through theweight accommodation part 38 and the bearingaccommodation part 40 along the drivingshaft 18. Theweight accommodation part 38 accommodates a balance weight 42 rotating integrally with the drivingshaft 18. In addition, the bearingaccommodation part 40 accommodates the bearing 26 rotatably supporting one end side of the drivingshaft 18. In addition, the throughhole 41 accommodates the drivingshaft 18 with a sufficient clearance left. - A suction chamber 45 for sucking, via a
suction route 44, the refrigerant introduced from asuction opening 43, which will be described later, is formed between the outerperipheral wall 11b of the fixedscroll 11 and the outermost peripheral part of thespiral wall 21c of the orbitingscroll 21. In addition, adischarge chamber 47 is formed between the fixedscroll 11 and arear end wall 46 of the compression mechanismaccommodation housing member 5 in the rear of the fixedscroll 11 in thehousing 2. The refrigerant gas compressed by thecompression chamber 37 is discharged to thisdischarge chamber 47 via adischarge hole 48 formed substantially at the center of the fixedscroll 11. The refrigerant gas having been discharged to thedischarge chamber 47 is press-fed to an external refrigerant circuit via adischarge opening 50. - The
motor fixing part 12, which is formed ahead of theend plate 13 of the motoraccommodation housing member 6, accommodates thestator 16 and arotor 51 constituting theelectric motor 4. Thestator 16 includes a cylindrical iron core and a coil wound therearound and thestator 16 is fixed to the inner surface of the housing 2 (motor accommodation housing member 6). In addition, therotor 51 including a magnet is fixed to the outer peripheral side of the drivingshaft 18 and rotatably accommodated within thestator 16. Therotor 51 is rotated integrally with the drivingshaft 18 by a rotary magnetic force generated by thestator 16. - The inverter device to be accommodated in the inverter
accommodation housing member 7 is electrically connected to thestator 16 via a terminal (airtight terminal) attached to a through hole (not illustrated) formed in theend plate 24 and supplies electricity to theelectric motor 4. - The
suction opening 43 through which refrigerant gas is sucked to themotor accommodation part 30 is formed in the side surface of the housing 2 (motor accommodation housing member 6). The refrigerant having flowed into themotor accommodation part 30 through thesuction opening 43 is introduced to the suction chamber 45 via thesuction route 44. Thesuction route 44 includes the clearance between thestator 16 and the housing 2 (motor accommodation housing member 6), holes 52 formed in theend plate 13, the clearance formed between the fixedscroll 11 and thehousing 2, and the like. - On the inner peripheral surface of the motor
accommodation housing member 6, as illustrated inFigs. 1 and3 ,stator contact parts 53 in contact with thestator 16 and statornon-contact parts 54 not in contact with thestator 16 are alternately formed in the circumferential direction. The outer peripheral part of thestator 16 is fixed to thestator contact parts 53 by close-fitting (such as press-fitting or shrink-fitting). This fixes thestator 16 to the housing 2 (motor accommodation housing member 6). The clearance between thestator 16 and the housing 2 (motor accommodation housing member 6) that configures part of thesuction route 44 is formed by the clearance between the inner walls of the statornon-contact parts 54 and the outer peripheral part of thestator 16. - In the embodiment, six pairs of the
stator contact part 53 and the statornon-contact part 54 are formed in the circumferential direction at intervals of 60 degrees. The length in the circumferential direction of thestator contact part 53 is relatively smaller than the length in the circumferential direction of the stator non-contact part 54 (the length of thestator contact part 53 has a center angle of approximately 20 degrees and the length of the statornon-contact part 54 has a center angle of approximately 40 degrees). - In addition, the
end plate 13 of the motoraccommodation housing member 6 is provided with theholes 52 communicating themotor accommodation part 30 with the compressionmechanism accommodation part 28. The refrigerant having flowed through thesuction opening 43 into themotor accommodation part 30 is introduced to the suction chamber 45 through theholes 52. - In addition, the
holes 52 are formed in theend plate 13 so as to be positioned radially outward ofpins 55 of a rotation prevention mechanism, which will be described later. The plurality ofholes 52 are formed in positions radially inward of fivestator contact parts 53 and substantially aligned with the fivestator contact parts 53 in the circumferential direction (positions having substantially the same phase) so as to correspond to the fivestator contact parts 53. In this example, theholes 52 correspond to only the fivestator contact parts 53 of the sixstator contact parts 53 and are formed as long holes extending in the circumferential direction of theend plate 13. - A
bolt hole 56 through which ashaft part 10a of the tightening bolt 10 passes is formed between thestator contact parts end plate 13. The tightening bolts 10 having theshaft parts 10a passing through the bolt holes 56 are used to fix the motoraccommodation housing member 6 and the inverteraccommodation housing member 7. Theshaft parts 10a of the tightening bolts 10 are fitted to thebolt accommodation parts 17 formed partially in thelow rigidity part 14 with a clearance left. Thebolt accommodation parts 17 are formed in the parts of thelow rigidity part 14 into which theshaft parts 10a of the tightening bolts 10 are inserted. Thebolt accommodation parts 17 project radially outward of theconstriction part 15 of thelow rigidity part 14, cover theshaft parts 10a of the tightening bolts 10 so that theshaft parts 10a of the tightening bolts 10 are not exposed to outside air, and protect theshaft parts 10a of the tightening bolts 10. As manybolt accommodation parts 17 as the tightening bolts 10 are formed and have a substantially circular cross section to improve the rigidity in the twist direction of thelow rigidity part 14. - The surface of the
end plate 13 close to themotor accommodation part 30 is provided integrally with reinforcingribs 57 for reinforcing theend plate 13 extending from theshaft supporting part 20 to the inner peripheral surface of thelow rigidity part 14 in the radial direction. The plurality of reinforcingribs 57 are formed at substantially regular intervals in the circumferential direction in positions corresponding to the statornon-contact parts 54 in the shaft direction, that is, in the positions substantially aligned with the statornon-contact parts 54 in the circumferential direction (in the positions having substantially the same phase) (six reinforcingribs 57 are provided in the circumferential direction so as to correspond to the number of thepins 55, which will be described later) . Accordingly, the reinforcingribs 57 are formed so that their positions in the circumferential direction are not aligned with the stator contact parts 53 (so that they do not have the same phase) to prevent the direct transfer of the stress generated by the deformation of thestator contact parts 53. - As illustrated in
Fig. 3(b) , the positioning pins 33 for positioning the fixedscroll 11 with respect to theend plate 13 are provided on avirtual circle 58 including theholes 52 and are fixed by being press-fitted intopin mounting holes 60 formed in theend plate 13. - According to the above structure, in the
compression mechanism 3, when therotor 51 and the drivingshaft 18 rotate integrally with each other, the orbitingscroll 21 is driven via theeccentric shaft 36 that rotates integrally with the drivingshaft 18 and the orbitingscroll 21 revolves about the shaft center of the drivingshaft 18. This introduces the refrigerant sucked to themotor accommodation part 30 through thesuction opening 43 to the suction chamber 45 via theholes 52 of theend plate 13 after passing through the clearance between the statornon-contact parts 54 around the rotor and thestator 16 and the clearance between the coils of thestator 16. Thecompression chamber 37 of thecompression mechanism 3 is moved from the outer peripheral sides of thespiral wall 11c of the fixedscroll 11 and thespiral wall 21c of the orbitingscroll 21 toward the center while gradually reducing its volume by the revolving motion of the orbitingscroll 21. As a result, the refrigerant gas sucked to thecompression chamber 37 from the suction chamber 45 is compressed as the orbitingscroll 21 revolves. The compressed refrigerant gas is discharged to thedischarge chamber 47 via thedischarge hole 48 formed in the board 11a of the fixedscroll 11 and fed to an external refrigerant circuit through thedischarge chamber 47 via thedischarge opening 50. - Since a rotation force is generated in the
orbiting scroll 21 as the drivingshaft 18 rotates in the electrically driven scroll compressor 1 described above, the orbitingscroll 21 needs to be revolved about the shaft center of the drivingshaft 18 in the state in which the rotation of the orbitingscroll 21 is restricted. Therefore, the electrically driven scroll compressor 1 according to the embodiment is provided with a rotation prevention mechanism for engaging thepins 55 between theboard 21a of the orbitingscroll 21 and theend plate 13 of the motoraccommodation housing member 6. - In the embodiment, a pin and ring coupling is adopted as the rotation prevention mechanism and this coupling includes a plurality of the
pins 55 disposed in the circumferential direction, a plurality ofring members 61 engaged onto thepins 55, and a plurality of cylindricalconcave portions 62 accommodating thering members 61. - As illustrated in
Figs. 1 and2 , the cylindricalconcave portions 62 are depressions having a circular cross section formed in the back surface (surface facing the end plate 13) of theboard 21a of the orbitingscroll 21 and formed at regular intervals (intervals of 60 degrees in this example) around the periphery of the engagementconcave portion 34 of the orbitingscroll 21. Thering members 61 are annular components made of iron, have an outer diameter smaller than the inner diameter of the cylindricalconcave portions 62, and loosely engaged to the cylindricalconcave portions 62. In addition, the length in the shaft direction of thering members 61 is substantially identical to or smaller than the length in the shaft direction of the cylindricalconcave portions 62. - The
pins 55 are formed in cylinders made of iron, have an outer diameter smaller than the inner diameter of thering members 61, and are fixed at regular intervals to the orbiting scrollside end surface 22 facing the orbitingscroll 21 around theweight accommodation part 38 of theend plate 13 of the motoraccommodation housing member 6 so as to be aligned with the positions of the cylindricalconcave portions 62. In the embodiment, thepins 55 are fixed by being press-fitted to pin mount holes 63 formed in theend plate 13 and fixed to the back surface of the part of theend plate 13 in which the reinforcingribs 57 are formed. - Accordingly, although a rotation force is generated by the rotation of the driving
shaft 18, the motion of the orbitingscroll 21 is restricted because thepins 55 fixed to theend plate 13 make contact with the inner peripheral surfaces of thering members 61 in the cylindricalconcave portions 62 and thepins 55 are engaged to the cylindricalconcave portions 62 via thering members 61. As a result, the orbitingscroll 21 is allowed only to revolve about the shaft center of the drivingshaft 18 in the state in which rotation is restricted. - As described above , in the electrically driven scroll compressor 1 according to the invention, when the
stator 16 of theelectric motor 4 is fixed to themotor fixing part 12 of the motoraccommodation housing member 6 by close-fitting and themotor fixing part 12 undergoes diameter expansion deformation by thestator 16, thelow rigidity part 14 having rigidity smaller than in themotor fixing part 12 and theend plate 13 is elastically deformed by the diameter expansion deformation of themotor fixing part 12, the diameter expansion deformation of themotor fixing part 12 is absorbed by thelow rigidity part 14, and the stress (stress caused by the diameter expansion deformation of the motor fixing part 12) caused in the connection part between thelow rigidity part 14 and theend plate 13 becomes smaller than in the case in which thelow rigidity part 14 is not provided. As a result, in the electrically driven scroll compressor 1 according to the embodiment, since the deformation of theend plate 13 caused by the diameter expansion deformation of the motor fixing part 12 (such as the falling down of the orbiting scroll side end surface 22) can be suppressed and the accuracy of the supporting surface supporting the revolving motion of the orbitingscroll 21 can be improved, the orbitingscroll 21 can be revolved at high accuracy and the performance and reliability of the compressor can be improved. - In addition, in the electrically driven scroll compressor 1 according to the embodiment, since the
low rigidity part 14 is formed across the entire circumference in the circumferential direction of the motoraccommodation housing member 6, the diameter expansion deformation of themotor fixing part 12 can be evenly absorbed across the entire circumference in the circumferential direction of the motoraccommodation housing member 6 and an imbalanced stress is not generated in the circumferential direction of theend plate 13. - In addition, in the electrically driven scroll compressor 1 according to the embodiment, since the
low rigidity part 14 has theconstriction part 15 formed by recessing the part between themotor fixing part 12 and theend plate 13 radially inward, the length of thelow rigidity part 14 in the cross sectional view inFig. 1 is longer than the case in which theconstriction part 15 is not provided and thelow rigidity part 14 is easily deformed following the diameter expansion deformation of themotor fixing part 12. Accordingly, as compared with the case in which theconstriction part 15 is not provided in thelow rigidity part 14, the electrically driven scroll compressor 1 according to the embodiment can reduce the stress generated in the connection part between thelow rigidity part 14 and theend plate 13, further reducing the deformation of theend plate 13 caused by the diameter expansion deformation of themotor fixing part 12. - In addition, in the electrically driven scroll compressor 1 according to the embodiment, the
bolt accommodation parts 17 projecting radially outward are formed partially on theconstriction part 15 of thelow rigidity part 14, cover theshaft parts 10a of the tightening bolts 10 for fixing the motoraccommodation housing member 6 and the inverteraccommodation housing member 7 with thebolt accommodation parts 17 so that theshaft parts 10a of the tightening bolts 10 are not exposed to outside air, and protect theshaft parts 10a of the tightening bolts 10 using thebolt accommodation parts 17. Accordingly, reduction in durability caused by corrosion or the like of the tightening bolts 10 can be prevented and the rigidity in the twist direction of thelow rigidity part 14 of the motoraccommodation housing member 6 can be improved. - In addition, in the electrically driven scroll compressor 1 according to the embodiment, since a pin and ring coupling is used as the rotation prevention mechanism and the cylindrical
concave portions 62 are formed in theboard 21a of the orbitingscroll 21, the weight of the orbitingscroll 21 as a movable member can be reduced and the drivability of the orbitingscroll 21 can be improved. In addition, thepins 55 are press-fitted and fixed to theend plate 13 of the motoraccommodation housing member 6, which is a fixing member having rigidity higher than theboard 21a of the orbitingscroll 21. As a result, in the electrically driven scroll compressor 1 according to the embodiment , theend plate 13 hardly deforms when thepins 55 are press-fitted and, even when thepins 55 are engaged to the cylindricalconcave portions 62 via thering members 61 and thepins 55 receive loads in the radial direction, the parts to which thepins 55 are press-fitted are not deformed by the loads in the radial direction, thereby enabling the improvement of the assembly accuracy of the pins 55 (thepins 55 can be prevented from being slanted) . Accordingly, in the electrically driven scroll compressor 1 according to the embodiment, combined with the effects of improving the accuracy of the supporting surface for theend plate 13 described above, the orbitingscroll 21 can be revolved at high accuracy and the performance and reliability of the compressor can be further improved. - In addition, in the electrically driven scroll compressor 1 according to the embodiment, the
pins 55 are fixed to the parts of theend plate 13 in which the reinforcingribs 57 are formed. That is, since thepins 55 are fixed to the parts of theend plate 13 having high rigidity, it is possible to surely prevent the parts to which thepins 55 are press-fitted from being deformed when thepins 55 are press-fitted and fixed or loads in the radial direction are received. - In addition, in the electrically driven scroll compressor 1 according to the embodiment, since the positioning pins 33 for positioning the
end plate 13 and the fixedscroll 11 are provided in the positions (on thevirtual circle 58 including the plurality of the holes 52) radially outward of the shaft center and the positioning pins 33 are fixed to theend plate 13 prevented from being deformed by the function of thelow rigidity part 14, the fixedscroll 11 is positioned on theend plate 13 at high accuracy. As a result, the electrically driven scroll compressor 1 according to the embodiment can combine the fixedscroll 11 with the orbitingscroll 21 at high accuracy and, combined with various effects of the above embodiment, the performance and reliability of the compressor can be further improved. - Although the cylindrical
concave portions 62 are engaged onto thepins 55 via thering members 61 in the electrically driven scroll compressor 1 according to the embodiment, thering members 61 may be omitted to obtain the rotation prevention function. In such a case, the cylindricalconcave portions 62 may be directly engaged onto thepins 55. The electrically driven scroll compressor modified to have such a structure can obtain the same working effect as in the electrically driven scroll compressor 1 according to the embodiment. - In addition, although the
pins 55 of the rotation prevention mechanism are fixed to theend plate 13 and the cylindricalconcave portions 62 of the rotation prevention mechanism are formed in theorbiting scroll 21 in the electrically driven scroll compressor 1 according to the embodiment, the invention is not limited to the embodiment and thepins 55 may be fixed to theorbiting scroll 21 and the cylindricalconcave portions 62 may be formed in theend plate 13. - In addition, although a pin and ring coupling is used as the rotation prevention mechanism in the electrically driven scroll compressor 1 according to the embodiment, the rotation prevention mechanism other than a pin and ring coupling may be used.
-
- 1:
- electrically driven scroll compressor
- 3:
- compression mechanism
- 4:
- electric motor
- 5:
- compression mechanism accommodation housing member
- 6:
- motor accommodation housing member
- 7:
- inverter accommodation housing member
- 11:
- fixed scroll
- 12:
- motor fixing part
- 13:
- end plate
- 14:
- low rigidity part
- 16:
- stator
- 21:
- orbiting scroll
- 22:
- orbiting scroll side end surface
Claims (4)
- An electrically driven scroll compressor (1) comprising:a compression mechanism accommodation housing member (5) for accommodating a compression mechanism (3) that is a combination of a fixed scroll (11) and an orbiting scroll (21) ;a motor accommodation housing member (6) for accommodating an electric motor (4) for driving the compression mechanism (3); andan inverter accommodation housing member (7) for accommodating an inverter device for driving and controlling the electric motor (4),wherein the motor accommodation housing member (7) includes a cylindrical motor fixing part (12) to which a stator (16) of the electric motor (4) is fixed by close-fitting, an end plate (13) having an orbiting scroll side end surface (22) that is a support surface for the orbiting scroll (21), and a low rigidity part (14) for making connection between the motor fixing part (12) and the end plate (13) andwherein the low rigidity part (14) has rigidity lower than in the motor fixing part (12) and the end plate (13) and characterized in that the low rigidity part (14) has a constriction (15) part formed by recessing a part between the motor fixing part (12) and the end plate (13) of the motor accommodation housing member (6) radially inward.
- The electrically driven scroll compressor (1) according to claim 1,
wherein the low rigidity part (14) is formed across the entire circumference in a circumferential direction of the motor accommodation housing member (6). - The electrically driven scroll compressor (1) according to claim 1 or 2,
wherein the motor accommodation housing member (6) is fixed to the inverter accommodation housing member (7) by a plurality of bolts (10),
shaft parts of the bolts (10) are engaged to bolt accommodation parts (17) formed in part of the constriction part (15) with a clearance left, and
the bolt accommodation parts (17) project radially outward of the constriction part (15) and cover the shaft parts of the bolts (10). - The electrically driven scroll compressor (1) according to any one of claims 1 to 3,
wherein a pin (55) of a pin and ring coupling is attached to one of a surface facing the end plate (13) of the orbiting scroll (21) and the orbiting scroll side end surface (22) of the end plate (13), the pin and ring coupling being a rotation prevention mechanism for preventing rotation of the orbiting scroll (22), and
a cylindrical concave portion (62) is formed in the other of the surface facing the end plate (13) of the orbiting scroll (21) and the orbiting scroll side end surface (22) of the end plate (13), the cylindrical concave portion being engaged onto the pin (55), the cylindrical concave portion and the pin constituting the rotation prevention mechanism.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2014260226 | 2014-12-24 | ||
PCT/JP2015/085398 WO2016104336A1 (en) | 2014-12-24 | 2015-12-17 | Electrically driven scroll compressor |
Publications (3)
Publication Number | Publication Date |
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EP3239526A1 EP3239526A1 (en) | 2017-11-01 |
EP3239526A4 EP3239526A4 (en) | 2018-08-08 |
EP3239526B1 true EP3239526B1 (en) | 2019-08-14 |
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Application Number | Title | Priority Date | Filing Date |
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EP15872905.3A Active EP3239526B1 (en) | 2014-12-24 | 2015-12-17 | Electrically driven scroll compressor |
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EP (1) | EP3239526B1 (en) |
JP (1) | JP6587636B2 (en) |
CN (1) | CN107002676B (en) |
WO (1) | WO2016104336A1 (en) |
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US10683865B2 (en) | 2006-02-14 | 2020-06-16 | Air Squared, Inc. | Scroll type device incorporating spinning or co-rotating scrolls |
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US20130232975A1 (en) | 2011-08-09 | 2013-09-12 | Robert W. Saffer | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
US10508543B2 (en) | 2015-05-07 | 2019-12-17 | Air Squared, Inc. | Scroll device having a pressure plate |
US10865793B2 (en) | 2016-12-06 | 2020-12-15 | Air Squared, Inc. | Scroll type device having liquid cooling through idler shafts |
WO2019212598A1 (en) | 2018-05-04 | 2019-11-07 | Air Squared, Inc. | Liquid cooling of fixed and orbiting scroll compressor, expander or vacuum pump |
US20200025199A1 (en) | 2018-07-17 | 2020-01-23 | Air Squared, Inc. | Dual drive co-rotating spinning scroll compressor or expander |
US11067080B2 (en) | 2018-07-17 | 2021-07-20 | Air Squared, Inc. | Low cost scroll compressor or vacuum pump |
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KR20130094652A (en) * | 2012-02-16 | 2013-08-26 | 한라비스테온공조 주식회사 | Electronic compressor |
JP5867313B2 (en) * | 2012-06-28 | 2016-02-24 | 株式会社豊田自動織機 | Electric compressor |
JP6074203B2 (en) * | 2012-09-25 | 2017-02-01 | 株式会社ヴァレオジャパン | Scroll compressor |
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- 2015-12-17 JP JP2016566179A patent/JP6587636B2/en active Active
- 2015-12-17 WO PCT/JP2015/085398 patent/WO2016104336A1/en active Application Filing
- 2015-12-17 EP EP15872905.3A patent/EP3239526B1/en active Active
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EP3239526A4 (en) | 2018-08-08 |
JPWO2016104336A1 (en) | 2017-10-05 |
CN107002676B (en) | 2019-09-03 |
JP6587636B2 (en) | 2019-10-09 |
EP3239526A1 (en) | 2017-11-01 |
WO2016104336A1 (en) | 2016-06-30 |
CN107002676A (en) | 2017-08-01 |
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