US20150152864A1 - Scroll compressor - Google Patents
Scroll compressor Download PDFInfo
- Publication number
- US20150152864A1 US20150152864A1 US14/527,071 US201414527071A US2015152864A1 US 20150152864 A1 US20150152864 A1 US 20150152864A1 US 201414527071 A US201414527071 A US 201414527071A US 2015152864 A1 US2015152864 A1 US 2015152864A1
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- Prior art keywords
- scroll compressor
- balance weight
- frame
- sub
- cup
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Classifications
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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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/02—Rotary-piston machines or pumps 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
- F04C2/025—Rotary-piston machines or pumps 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 the moving and the stationary member having co-operating elements in spiral form
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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
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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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
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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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
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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
-
- 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
- F04C18/04—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 of internal-axis type
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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
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/18—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
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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
- 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
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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
- F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
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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
- F04C29/0021—Systems for the equilibration of forces acting on the pump
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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
- F04C29/02—Lubrication; Lubricant separation
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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
- F04C29/02—Lubrication; Lubricant separation
- F04C29/026—Lubricant separation
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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
- F04C29/04—Heating; Cooling; Heat insulation
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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
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/807—Balance weight, counterweight
Definitions
- the present invention relates to scroll compressors that reduce the amount of refrigerating machine oil discharged to the outside of a hermetic container.
- a forced oil supply passage ( 18 ) which communicates with the oil supply pump ( 8 ) is disposed to supply oil to the bearing ( 15 ) and a spiral groove ( 19 ) is formed on the outer peripheral surface of a rotor ( 31 ) of the motor ( 3 ) to downwardly return the oil supplied to the bearing ( 15 ) in a forcible manner such that the oil after lubrication can be returned to the oil supply pump without using a special oil separator while the oil is forcibly supplied to the bearing ( 15 ) disposed on the upper side.
- Patent Literature 1 Japanese Unexamined Patent Application Publication No. 5-302581 (for example, see FIG. 1)
- the fixed cup is not rotated even during driving period of the electric motor since the fixed cup is disposed on the upper end of the sub-frame which is fixed to the hermetic container. Further, the balance weight is surrounded by the fixed cup.
- FIG. 1 is a vertical cross-sectional view of a scroll compressor according to Embodiment 1 of the present invention.
- the motor rotor 5 a is disposed inside the motor stator 5 b , and the penetrating flow passage 5 f is formed in the motor rotor 5 a in the axis direction.
- the motor stator 5 b is disposed outside the motor rotor 5 a , and a motor stator coil 5 c is wound around the motor stator 5 b .
- a main shaft portion 6 b of the main shaft 6 is fixedly provided inside the motor rotor 5 a .
- the motor rotor 5 a rotates to cause the main shaft 6 to rotate and transmits a drive force to the compression mechanism 14 which is connected via the main shaft 6 .
- second notches 5 g are formed between the outer periphery of the motor stator 5 b and the hermetic container 10 to serve as passages for a mixed gas of the refrigerant and the refrigerating machine oil.
- An upper balance weight 15 a and a lower balance weight 15 b is fixed to the upper end face and the lower end face of the motor rotor 5 a , respectively, and in addition to the main shaft balance weight 6 f , those balance weights disposed at three positions keep the static balance and the dynamic balance. That is, those balance weights keep balance during shut down period of the electric motor 5 and offset the imbalance between the centrifugal force and the moment generated at the compression mechanism 14 during driving period of the electric motor 5 to keep balance. Further, an upper cup 17 is disposed to surround the upper balance weight 15 a at the upper end of the motor rotor 5 a , and a fixed cup 18 is disposed to surround the lower balance weight 15 b at the upper end of the sub-frame 8 .
- the fixed cup 18 is formed to separate a cup inside space 18 e which contains the lower balance weight 15 b therein and a cup outside space 18 f which does not contain the lower balance weight 15 b therein (which is located outside the fixed cup 18 ) in the space between the upper end of the sub-frame 8 and the lower balance weight 15 b . Further, as shown in FIG. 2 , a gap space 18 d is formed between the upper end of the fixed cup 18 and the lower end of the motor rotor 5 a.
- the outer peripheral surface of the motor stator 5 b is fixed to the hermetic container 10 by shrink-fitting, welding or the like, and the second notches 5 g are formed on the outer periphery to serve as passages for a mixed gas of the refrigerant and the refrigerating machine oil.
- glass terminals 10 a are disposed on the side face of the hermetic container 10 , and the lead wires 5 h which extend from the motor stator 5 b are connected to the glass terminals 10 a.
- the separated refrigerant gas flows through the gap space 18 d between the upper end of the fixed cup 18 and the lower end of the motor rotor 5 a and the penetrating flow passage 5 f of the motor rotor 5 a and is released to the outside of the hermetic container 10 through the discharge pipe 12 .
- the fixed cup 18 is formed of two parts in the scroll compressor.
- the fixed cup 18 is composed of a seat member 18 b for fixing to the sub-frame 8 and a cup member 18 a that surrounds the lower balance weight 15 b , and the cup member 18 a is connected to the seat member 18 b via a connection section 18 c.
- the seat member 18 b can be formed thick to retain the fixture strength and the cup member 18 a can be formed thin to save material cost.
- Embodiment 4 the scroll compressor according to Embodiment 4 will be described.
- the seat member 18 b and the cup member 18 a are welded in the scroll compressor.
- the cup member 18 a is connected to the seat member 18 b by welding at a connection section 18 c.
- the seat member 18 b and the cup member 18 a are connected by welding in the fixed cup 18 , it is possible to prevent the cup member 18 a from being detached from the seat member 18 b due to pressure difference between the sup inside space 18 e and the cup outside space 18 f.
- Embodiment 5 dimensions between the motor rotor 5 a and the fixed cup 18 in the scroll compressor are defined.
- FIG. 7 is a view which shows a relationship of a vertical cross-sectional area of the gap space of the scroll compressor and a circulation amount of the refrigerating machine oil according to Embodiment 5 of the present invention.
- the horizontal axis represents the vertical cross-sectional area of the gap space 18 d
- the vertical axis represents the circulation amount of the refrigerating machine oil in the refrigeration cycle during operating period of the scroll compressor.
- the dotted line represents the position of the vertical cross-sectional area of the penetrating flow passage 5 f of the motor rotor 5 a in FIG. 7 .
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
A scroll compressor includes a hermetic container in which a refrigeration machine oil is stored in a bottom area, a compression mechanism that compresses a refrigerant which is suctioned into the hermetic container, an electric motor which has a motor rotor and a motor stator and is configured to drive the compression mechanism which is connected thereto via a shaft, a sub-frame that is fixed to the hermetic container and supports the shaft in a rotatable manner from a lower side of the electric motor, a balance weight that is disposed on a lower end face of the motor rotor, and a fixed cup that is disposed on an upper end of the sub-frame and surrounds the balance weight.
Description
- The present invention relates to scroll compressors that reduce the amount of refrigerating machine oil discharged to the outside of a hermetic container.
- In scroll compressors that use a compression mechanism which is driven by an electric motor element to compress a refrigerant which is introduced in a hermetic container, some scroll compressors reduce the amount of refrigerating machine oil discharged to the outside of the hermetic container (for example, see
Patent Literatures 1 and 2). - In the scroll compressor described in
Patent Literature 1, a compression element (2) is positioned on the lower part in a vertical hermetic casing (1) and a motor (3) with a drive shaft (4) is positioned on the upper side of the compression element (2). A bearing (15) of the drive shaft (4) is disposed on the upper side of the motor and an oil supply pump (8) is disposed on the lower side of the drive shaft (4). A forced oil supply passage (18) which communicates with the oil supply pump (8) is disposed to supply oil to the bearing (15) and a spiral groove (19) is formed on the outer peripheral surface of a rotor (31) of the motor (3) to downwardly return the oil supplied to the bearing (15) in a forcible manner such that the oil after lubrication can be returned to the oil supply pump without using a special oil separator while the oil is forcibly supplied to the bearing (15) disposed on the upper side. - Further, the scroll compressor described in Patent Literature 2 includes a scroll compression mechanism (11) that compresses a refrigerant and a drive motor (13) that is connected to the scroll compression mechanism (11) via a drive shaft (15) to drive the scroll compression mechanism (11), which are housed in a casing (3), and the scroll compression mechanism (11) is supported by a main frame (21) in the casing (3), the drive shaft (15) of the drive motor (13) is supported by a bearing plate (8) in the casing (3), the bearing plate (8) has an opening (8E) that communicates upper and lower spaces of the bearing plate (8) and includes a cover (80) that covers the surrounding of the drive shaft (15) between the drive motor (13) and the bearing plate (8), and the cover (80) includes a plurality of cover members (80A, 80B) which are separated into such sizes that are allowed to pass through the opening (8E).
- [Patent Literature 1] Japanese Unexamined Patent Application Publication No. 5-302581 (for example, see FIG. 1)
- [Patent Literature 2] Japanese Unexamined Patent Application Publication No. 2013-47481 (for example, see FIG. 1)
- However, in conventional scroll compressors shown in
Patent Literatures 1 and 2, a balance weight disposed on the lower end of the rotor of the electric motor may be rotated due to driving of the electric motor during start of operation. Then, when the liquid level of the refrigerating machine oil or the mixed liquid of the refrigerating machine oil and the refrigerant is around or above the lower end of the electric motor element, the refrigerating machine oil or the mixed liquid of the refrigerating machine oil and the refrigerant may be mixed by the balance weight. This causes a problem that the refrigerating machine oil is discharged to the outside of the hermetic container, which results in decreased reliability of the bearing, and the amount of oil in the refrigeration cycle increases, which results in decreased cycle efficiency. - The present invention has been made to solve the above problem and an object of the invention is to provide a scroll compressor that prevents a refrigerating machine oil or a mixed liquid of refrigerating machine oil and refrigerant from being mixed during driving period of an electric motor and reduces the amount of refrigerating machine oil discharged to the outside of a hermetic container.
- A scroll compressor according to the present invention includes a hermetic container in which a refrigeration machine oil is stored in a bottom area, a compression mechanism that compresses a refrigerant which is suctioned into the hermetic container, an electric motor which has a motor rotor and a motor stator and is configured to drive the compression mechanism which is connected thereto via a shaft, a sub-frame that is fixed to the hermetic container and supports the shaft in a rotatable manner from a lower side of the electric motor, a balance weight that is disposed on a lower end face of the motor rotor, and a fixed cup that is disposed on an upper end of the sub-frame and surrounds the balance weight.
- According to the scroll compressor of the present invention, the fixed cup is not rotated even during driving period of the electric motor since the fixed cup is disposed on the upper end of the sub-frame which is fixed to the hermetic container. Further, the balance weight is surrounded by the fixed cup.
- Accordingly, the refrigerating machine oil or the mixed liquid of the refrigerating machine oil and the refrigerant can be prevented from being mixed by rotation of the balance weight, the amount of the refrigerating machine oil discharged to the outside of the hermetic container can be reduced, the reliability of the bearings is improved, and the cycle efficiency of the refrigeration cycle is improved.
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FIG. 1 is a vertical cross-sectional view of a scroll compressor according toEmbodiment 1 of the present invention. -
FIG. 2 is an enlarged view of an essential part ofFIG. 1 . -
FIG. 3 is a transverse cross-sectional view of a guide frame taken along the line A-A ofFIG. 1 . -
FIG. 4 is a transverse cross-sectional view of a motor stator taken along the line B-B ofFIG. 1 . -
FIG. 5 is a vertical cross-sectional view of a fixed cup according to Embodiment 3 of the present invention. -
FIG. 6A is a vertical cross-sectional view which shows a penetrating flow passage of a motor rotor according toEmbodiment 5 of the present invention. -
FIG. 6B is a transverse cross-sectional view which shows a penetrating flow passage of a motor rotor according toEmbodiment 5 of the present invention. -
FIG. 7 is a view which shows a relationship of a vertical cross-sectional area of a gap space of the scroll compressor and a circulation amount of a refrigerating machine oil according toEmbodiment 5 of the present invention. - Embodiments of the invention will be described below with reference to the drawings. It should be noted that the present invention is not limited by the following Embodiments. In the accompanying drawings, the size relationship between components may be different from the actual relationship.
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FIG. 1 is a vertical cross-sectional view of ascroll compressor 100 according toEmbodiment 1 of the present invention, andFIG. 2 is an enlarged view of an essential part ofFIG. 1 . - The
scroll compressor 100 according toEmbodiment 1 of the present invention includes a compression mechanism 14 which has afixed scroll 1 and a rocking scroll 2 in ahermetic container 10 which is in the shape of a hermetic dome and is configured to compress a refrigerant, and anelectric motor 5 which has amotor rotor 5 a and amotor stator 5 b and is configured to drive the compression mechanism 14 which is connected to theelectric motor 5 via a main shaft 6. - The
fixed scroll 1 is composed of a base plate 1 a and a scroll lap 1 b, and an outer periphery of thefixed scroll 1 is fastened to aguide frame 4 by using a bolt (not shown in the figure). The scroll lap 1 b is disposed on one side (the lower side inFIG. 1 ) of the base plate 1 a, and oldham guiding grooves 1 c are formed on the outer periphery of thefixed scroll 1 at two positions which are substantially on a straight line. Further, a fixed key 9 a of anoldham mechanism 9 engages the oldham guiding groove 1 c in a reciprocatingly slidable manner. Still further, adischarge port 1 d is formed at the center of the base plate 1 a through which a refrigerant is discharged. In addition, asuction pipe 13 is press fit into thefixed scroll 1 through thehermetic container 10 with a suction port 1 e being located inside thefixed scroll 1. - The rocking scroll 2 is composed of a
base plate 2 a and a scroll lap 2 b. The scroll lap 2 b which has a shape substantially the same as that of the scroll lap 1 b of thefixed scroll 1 is disposed on one side (the upper side inFIG. 1 ) of thebase plate 2 a. The scroll lap 1 b of thefixed scroll 1 and the scroll lap 2 b of the rocking scroll 2 geometrically form acompression chamber 1 f. The refrigerant suctioned into thehermetic container 10 is compressed in response to change in volume of thecompression chamber 1 f. Further, aboss 2 d in a hollow cylindrical shape is formed at the center of a surface (the lower side inFIG. 1 , which is hereinafter referred to as the lower surface) of thebase plate 2 a opposite to a surface on which the scroll lap 2 b is disposed. Theboss 2 d rotatably supports a rockingshaft section 6 a on the upper end of the main shaft 6. In addition, athrust surface 2 f is formed around the circumference of theboss 2 d to be in sliding contact with the thrust bearing 3 a of a compliant frame 3. - Oldham guiding grooves 2 c which has a phase difference of 90 degrees from the oldham guiding grooves 1 c of the fixed
scroll 1 are formed on the outer periphery of thebase plate 2 a of the rocking scroll 2 at two positions which are substantially on a straight line. Further, a rockingkey 9 b of theoldham mechanism 9 engages the oldham guiding groove 2 c in a reciprocatingly slidable manner. In addition, a rocking scroll bleeding hole 2 g which penetrates thecompression chamber 1 f and thethrust surface 2 f is formed on thebase plate 2 a so that a refrigerant gas is extracted during compression through the bleeding hole 2 g and is guided to thethrust surface 2 f. - The compliant frame 3 is provided with upper and lower
cylindrical surfaces 3 p, 3 s formed on the outer periphery of the compliant frame 3 which are radially supported bycylindrical surfaces 4 c, 4 d formed on the inner periphery of theguide frame 4. The compliant frame 3 is also provided with a main shaft bearing 3 c and an auxiliary main shaft bearing 3 d at the center of the compliant frame 3 such that the main shaft bearing 3 c and the auxiliary main shaft bearing 3 d radially support the main shaft 6 which is rotated by theelectric motor 5. Further, a communication hole 3 e is formed to penetrate the thrust bearing 3 a in the axis direction, and the opening 3 t of the thrust bearing 3 a is located at a position which faces the rocking scroll bleeding hole 2 g. - A
slide surface 3 b on which an oldham mechanismannular section 9 c reciprocatingly slides is formed outside the thrust bearing 3 a of the compliant frame 3, and a communication hole 3 f that communicates a base platecircumferential space 2 k and a frameupper space 4 a is provided so as to communicate with the inside of the oldham mechanismannular section 9 c. Further, the compliant frame 3 is provided with an intermediate pressure regulating valve 3 g that adjusts a pressure of a bossouter diameter space 2 n and an intermediate pressure regulatingvalve guard 3h. Further, an intermediate pressure regulatingvalve space 3 n is formed to house an intermediate pressure regulatingvalve spring 3 k. The intermediate pressure regulatingvalve spring 3 k is housed in a collapsed state which is shorter than its natural length. -
FIG. 3 is a transverse cross-sectional view of theguide frame 4 taken along the line A-A ofFIG. 1 . - As shown in
FIG. 3 , the outer peripheral surface of theguide frame 4 is fixed to thehermetic container 10 by shrink-fitting, welding or the like, andfirst notches 4 f are formed on the outer periphery to serve as passages for a mixed gas of the refrigerant and the refrigerating machine oil. Further, as shown inFIG. 1 , thefirst notches 4 f are formed at positions on the opposite side of thedischarge pipe 12. Afirst discharge passage 4 g is formed to extend from the center on the lower end of theguide frame 4 to the side face, and thedischarge pipe 12 is disposed to penetrate thehermetic container 10 with theend portion 12 a being housed in thefirst discharge passage 4 g. Acover 16 which has anopening 4 h and forms asecond discharge passage 16 a and anopening 16 b is disposed on one side (the lower side inFIG. 1 ) of theguide frame 4. - A frame lower space 4 b is formed by the inner surface of the
guide frame 4 and the outer surface of the compliant frame 3, and the upper side and the lower side of the frame lower space 4 b are partitioned by an upperring seal member 7 a and a lower ring seal member 7 b, respectively. Although ring-shaped seal grooves are formed at two positions on the inner peripheral surface of theguide frame 4 to house the upperring seal member 7 a and the lower ring seal member 7 b, the seal groove may be formed on the outer peripheral surface of the compliant frame 3. The frame lower space 4 b communicates only with the communication hole 3 e of the compliant frame 3 and is configured to seal the refrigerant gas during compression which is supplied through the rocking scroll bleeding hole 2 g. Further, a space around the circumference of the thrust bearing 3 a, which is surrounded by thebase plate 2 a of the rocking scroll 2 and the compliant frame 3 on its upper and lower sides, that is, a base platecircumferential space 2 k is a lower pressure space of a suction gas atmosphere (suction pressure). - The
motor rotor 5 a is disposed inside themotor stator 5 b, and the penetratingflow passage 5 f is formed in themotor rotor 5 a in the axis direction. Themotor stator 5 b is disposed outside themotor rotor 5 a, and amotor stator coil 5 c is wound around themotor stator 5 b. Amain shaft portion 6 b of the main shaft 6 is fixedly provided inside themotor rotor 5 a. Themotor rotor 5 a rotates to cause the main shaft 6 to rotate and transmits a drive force to the compression mechanism 14 which is connected via the main shaft 6. Further,second notches 5 g are formed between the outer periphery of themotor stator 5 b and thehermetic container 10 to serve as passages for a mixed gas of the refrigerant and the refrigerating machine oil. - A rocking
shaft portion 6 a which is rotatably supported by the rocking bearing 2 e of the rocking scroll 2 is formed on the upper end of the main shaft 6, and a mainshaft balance weight 6 f is shrink-fitted under the rockingshaft portion 6 a. Further, themain shaft portion 6 b which is rotatably supported by the main shaft bearing 3 d and the auxiliary main shaft bearing 3 d of the compliant frame 3 is formed under the mainshaft balance weight 6 f. Still further, a sub-shaft portion 6 c which is rotatably supported by a sub-shaft bearing 8 e of thesub-frame 8 is formed on the lower end of the main shaft 6, and the outer peripheral surface of thesub-frame 8 is fixed to thehermetic container 10 by shrink-fitting, welding or the like. Themotor rotor 5 a is shrink-fitted between the sub-shaft portion 6 c and themain shaft portion 6 b. The refrigerating machine oil is stored in anoil sump 11 at the bottom of thehermetic container 10, and the refrigerating machine oil is suctioned through anoil supply port 6 d which is formed on the lower end face of the main shaft 6 by using an oil supply mechanism disposed in the main shaft 6. - An
upper balance weight 15 a and alower balance weight 15 b is fixed to the upper end face and the lower end face of themotor rotor 5 a, respectively, and in addition to the mainshaft balance weight 6 f, those balance weights disposed at three positions keep the static balance and the dynamic balance. That is, those balance weights keep balance during shut down period of theelectric motor 5 and offset the imbalance between the centrifugal force and the moment generated at the compression mechanism 14 during driving period of theelectric motor 5 to keep balance. Further, anupper cup 17 is disposed to surround theupper balance weight 15 a at the upper end of themotor rotor 5 a, and a fixedcup 18 is disposed to surround thelower balance weight 15 b at the upper end of thesub-frame 8. The fixedcup 18 is formed to separate a cup insidespace 18 e which contains thelower balance weight 15 b therein and a cup outsidespace 18 f which does not contain thelower balance weight 15 b therein (which is located outside the fixed cup 18) in the space between the upper end of thesub-frame 8 and thelower balance weight 15 b. Further, as shown inFIG. 2 , agap space 18 d is formed between the upper end of the fixedcup 18 and the lower end of themotor rotor 5 a. -
FIG. 4 is a transverse cross-sectional view of themotor stator 5 b taken along the line B-B ofFIG. 1 . - As shown in
FIG. 4 , the outer peripheral surface of themotor stator 5 b is fixed to thehermetic container 10 by shrink-fitting, welding or the like, and thesecond notches 5 g are formed on the outer periphery to serve as passages for a mixed gas of the refrigerant and the refrigerating machine oil. Further, as shown inFIG. 1 ,glass terminals 10 a are disposed on the side face of thehermetic container 10, and thelead wires 5 h which extend from themotor stator 5 b are connected to theglass terminals 10 a. - Next, an operation of the
scroll compressor 100 according toEmbodiment 1 during operating period will be described. - The suction refrigerant is suctioned through the
suction pipe 13 during starting and operating period of thescroll compressor 100 and enters thecompression chamber 1 f formed by the scroll lap 1 b of the fixedscroll 1 and the scroll lap 2 b of the rocking scroll 2. The rocking scroll 2 which is driven by theelectric motor 5 reduces the volume of thecompression chamber 1 f as the eccentric rotation movement. This compression stroke causes the suction refrigerant to be under high pressure. Further, in this compression stroke, the refrigerant gas of the intermediate pressure during compression is guided from the rocking scroll bleeding hole 2 g of the rocking scroll 2 to the frame lower space 4 b via the communication hole 3 e of the compliant frame 3 so as to keep the intermediate pressure atmosphere of the frame lower space 4 b. - After the compression stroke, the mixed gas of the refrigerant and the refrigerating machine oil which is suctioned from the suction hole 1 e and is discharged from the
discharge port 1 d of the fixedscroll 1 is guided to the bottom of thehermetic container 10 through thefirst notches 4 f formed on the outer periphery of theguide frame 4 and thesecond notches 5 g formed on the outer periphery of themotor stator 5 b. The mixed gas of the refrigerant and the refrigerating machine oil are separated in the course of being guided to the bottom of thehermetic container 10. The separated refrigerant gas flows through thegap space 18 d between the upper end of the fixedcup 18 and the lower end of themotor rotor 5 a and the penetratingflow passage 5 f of themotor rotor 5 a and is released to the outside of thehermetic container 10 through thedischarge pipe 12. - Next, a state of the
scroll compressor 100 according toEmbodiment 1 during shut down period will be described. - In the shut down period of the
scroll compressor 100, when the temperature of thescroll compressor 100 is low, the refrigerant in the refrigeration cycle is liquefied and flows into thescroll compressor 100 and is mixed with the refrigerating machine oil. The liquid level of the mixed liquid comes near the lower end of themotor stator coil 5 c which is wound around themotor stator 5 b or above the lower end of themotor stator coil 5 c. - Next, an operation of the
scroll compressor 100 according toEmbodiment 1 during start of operation will be described. - Since the fixed
cup 18 is disposed on the upper end of thesub-frame 8, the fixedcup 18 does not rotate even during driving period of theelectric motor 5. Further, thelower balance weight 15 b is surrounded by the fixedcup 18. Accordingly, the refrigerating machine oil or the mixed liquid of the refrigerating machine oil and the refrigerant can be prevented from being mixed by rotation of thelower balance weight 15 b, the amount of the refrigerating machine oil discharged to the outside of the hermetic container can be reduced, the reliability of all the bearings (rocking bearing 2 e, thrust bearing 3 a, main shaft bearing 3 c, auxiliary main shaft bearing 3 d,sub-shaft bearing 8 a) is improved, and the cycle efficiency of the refrigeration cycle is improved. - The refrigerating machine oil may be miscible or immiscible with the refrigerant. In the case of the refrigerating machine oil miscible with the refrigerant, the refrigerating machine oil released into the refrigeration cycle is returned to the
scroll compressor 100 along with the refrigerant flowing from the refrigeration cycle during shut down period of thescroll compressor 100. As a result, the liquid level of the mixed liquid becomes higher than that of the immiscible refrigerating machine oil. Accordingly, the fixedcup 18 is more effective when used for the miscible refrigerating machine oil. - Next, the scroll compressor according to Embodiment 2 will be described. In Embodiment 2, the refrigerating machine oil is sealed in the scroll compressor with the liquid level being above the lower end of the
motor stator coil 5 c which is wound around themotor stator 5 b. - In the following description, the configuration and operation which are the same as those of
Embodiment 1 will not be described. - When the scroll compressor is installed in air conditioning apparatuses or refrigerating machines which include a large refrigeration cycle, the amount of refrigerating machine oil sealed in the scroll compressor is increased in accordance with the increased amount of refrigerant in the refrigeration cycle so that the liquid level of the refrigerating machine oil is above the lower end of the
electric motor 5. - As described above, even when the refrigerating machine oil is sealed with the liquid level thereof being above the lower end of the
electric motor 5, the refrigerating machine oil or the mixed liquid of the refrigerating machine oil and the refrigerant can be prevented from being mixed by rotation of thelower balance weight 15 b, the amount of the refrigerating machine oil discharged to the outside of the hermetic container can be reduced, the reliability of all the bearings is improved, and the cycle efficiency of the refrigeration cycle is improved, since thelower balance weight 15 b is surrounded by the fixedcup 18 disposed on the upper end of thesub-frame 8. - Next, the scroll compressor according to Embodiment 3 will be described. In Embodiment 3, the fixed
cup 18 is formed of two parts in the scroll compressor. - In the following description, the configuration and operation which are the same as those of
Embodiment 1 or 2 will not be described. -
FIG. 5 is a vertical cross-sectional view of the fixedcup 18 according to Embodiment 3 of the present invention. - As shown in
FIG. 5 , the fixedcup 18 is composed of aseat member 18 b for fixing to thesub-frame 8 and a cup member 18 a that surrounds thelower balance weight 15 b, and the cup member 18 a is connected to theseat member 18 b via aconnection section 18 c. - As described above, since the fixed
cup 18 is composed of two members of theseat member 18 b and the cup member 18 a, theseat member 18 b can be formed thick to retain the fixture strength and the cup member 18 a can be formed thin to save material cost. - Next, the scroll compressor according to
Embodiment 4 will be described. InEmbodiment 4, theseat member 18 b and the cup member 18 a are welded in the scroll compressor. - In the following description, the configuration and operation which are the same as those of any of
Embodiments 1 to 3 will not be described. - In
FIG. 5 , the cup member 18 a is connected to theseat member 18 b by welding at aconnection section 18 c. - As described above, since the
seat member 18 b and the cup member 18 a are connected by welding in the fixedcup 18, it is possible to prevent the cup member 18 a from being detached from theseat member 18 b due to pressure difference between the sup insidespace 18 e and the cup outsidespace 18 f. - Next, the scroll compressor according to
Embodiment 5 will be described. InEmbodiment 5, dimensions between themotor rotor 5 a and the fixedcup 18 in the scroll compressor are defined. - In the following description, the configuration and operation which are the same as those of any of
Embodiments 1 to 4 will not be described. -
FIG. 6A is a vertical cross-sectional view which shows the penetratingflow passage 5 f of themotor rotor 5 a according toEmbodiment 5 of the present invention.FIG. 6B is a transverse cross-sectional view which shows the penetratingflow passage 5 f of themotor rotor 5 a according toEmbodiment 5 of the present invention. - In the scroll compressor according to
Embodiment 5 of the present invention, dimensions of the fixedcup 18 are defined such that the vertical cross-sectional area of thegap space 18 d between the upper end of the fixedcup 18 shown inFIG. 2 and the lower end of themotor rotor 5 a is larger than the vertical cross-sectional area of the penetratingflow passage 5 f of themotor rotor 5 a shown inFIGS. 6A , 6B and 7. -
FIG. 7 is a view which shows a relationship of a vertical cross-sectional area of the gap space of the scroll compressor and a circulation amount of the refrigerating machine oil according toEmbodiment 5 of the present invention. InFIG. 7 , the horizontal axis represents the vertical cross-sectional area of thegap space 18 d, and the vertical axis represents the circulation amount of the refrigerating machine oil in the refrigeration cycle during operating period of the scroll compressor. The dotted line represents the position of the vertical cross-sectional area of the penetratingflow passage 5 f of themotor rotor 5 a inFIG. 7 . - As shown in
FIG. 7 , when the vertical cross-sectional area of thegap space 18 d becomes larger than the the vertical cross-sectional area of the penetratingflow passage 5 f of themotor rotor 5 a, the circulation amount of the refrigerating machine oil during operating period of the scroll compressor decreases. Based on this relationship, the amount of the refrigerating machine oil released from the scroll compressor into the refrigeration cycle during operating period can be reduced by defining a height dimension or a diameter dimension of the fixedcup 18 such that the vertical cross-sectional area of thegap space 18 d is larger than the the vertical cross-sectional area of the penetratingflow passage 5 f of themotor rotor 5 a. Accordingly, the reliability of all the bearings is improved, and the cycle efficiency of the refrigeration cycle is improved. - 1 fixed scroll; 1 a base plate (of the fixed scroll); 1 b scroll lap (of the fixed scroll); 1 c oldham guiding groove (of the fixed scroll); 1 d discharge port; 1 e suction port; 1 f compression chamber 2 rocking scroll; 2 a base plate (of the rocking scroll); 2 b scroll lap (of the rocking scroll); 2 c oldham guiding groove (of the rocking scroll); 2 d boss; 2 e rocking bearing; 2 f thrust surface; 2 g rocking scroll air bleed hole; 2 k base plate circumferential space; 2 n boss outer diameter space; 3 compliant frame; 3 a thrust bearing; 3 b slide surface; 3 c main shaft bearing; 3 d auxiliary main shaft bearing; 3 e communication hole; 3 f communication hole; 3 g intermediate pressure regulating valve; 3 h intermediate pressure regulating valve guard; 3 k intermediate pressure regulating spring; 3n intermediate pressure regulating valve space; 3 p cylindrical surface (of the compliant frame); 3 t thrust bearing opening; 4 guide frame; 4 a frame upper space; 4 b frame lower space; 4 c cylindrical surface (of the guide frame); 4 f first notch; 4 g first discharge passage; 4 h opening; 5 electric motor; 5 a motor rotor; 5 b motor stator; 5 c motor stator coil; 5 f penetrating flow passage; 5 g second notch; 5 h lead wire; 6 main shaft; 6 a rocking shaft portion; 6 b main shaft portion; 6 c sub-shaft portion; 6 d oil supply port; 6 f main shaft balance weight; 7 a upper ring seal member; 7 b upper ring seal member; 8 sub-frame; 8 a sub-shaft bearing; 9 oldham mechanism; 9 a fixed key of the oldham mechanism; 9 b rocking key of the oldham mechanism; 9 c oldham mechanism annular section; 10 hermetic container; 10 a glass terminal; 11 oil sump; 12 discharge pipe; 12 a end portion (of the discharge pipe); 13 suction pipe; 14 compression mechanism; 15 balance weight; 15 a upper balance weight; 15 b lower balance weight; 16 cover; 16 a second discharge passage; 16 b opening; 17 upper cup; 18 fixed cup; 18 a cup member; 18 b seat member; 18 c connection section; 18 d gap space; 18 e cup inside space; 18 f cup outside space; 100 scroll compressor
Claims (13)
1. A scroll compressor comprising:
a hermetic container in which a refrigeration machine oil is stored in a bottom area of the hermetic container;
a compression mechanism that compresses a refrigerant which is suctioned into the hermetic container;
an electric motor which has a motor rotor and a motor stator and is configured to drive the compression mechanism which is connected to the electric motor via a shaft;
a sub-frame that is fixed to the hermetic container and supports the shaft in a rotatable manner from a lower side of the electric motor;
a balance weight that is disposed on a lower end face of the motor rotor; and
a fixed cup that is disposed on an upper end of the sub-frame and surrounds the balance weight.
2. The scroll compressor of claim 1 , wherein the fixed cup separates an inside space which contains the balance weight therein and an outside space which does not contain the balance weight therein in a space between the upper end of the sub-frame and the balance weight.
3. The scroll compressor of claim 1 , wherein the refrigerating machine oil is sealed with the liquid level thereof being above the lower end of the electric motor.
4. The scroll compressor of claim 2 , wherein the refrigerating machine oil is sealed with the liquid level thereof being above the lower end of the electric motor.
5. The scroll compressor of claim 1 , wherein the fixed cup is formed by connecting a seat member for fixing to the sub-frame and a cup member that surrounds the balance weight.
6. The scroll compressor of claim 2 , wherein the fixed cup is formed by connecting a seat member for fixing to the sub-frame and a cup member that surrounds the balance weight.
7. The scroll compressor of claim 3 , wherein the fixed cup is formed by connecting a seat member for fixing to the sub-frame and a cup member that surrounds the balance weight.
8. The scroll compressor of claim 4 , wherein the fixed cup is formed by connecting a seat member for fixing to the sub-frame and a cup member that surrounds the balance weight.
9. The scroll compressor of claim 5 , wherein the seat member for fixing to the sub-frame and the cup member that surrounds the balance weight are connected by welding.
10. The scroll compressor of claim 6 , wherein the seat member for fixing to the sub-frame and the cup member that surrounds the balance weight are connected by welding.
11. The scroll compressor of claim 7 , wherein the seat member for fixing to the sub-frame and the cup member that surrounds the balance weight are connected by welding.
12. The scroll compressor of claim 8 , wherein the seat member for fixing to the sub-frame and the cup member that surrounds the balance weight are connected by welding.
13. The scroll compressor of claim 1 , wherein a penetrating flow passage is formed in the motor rotor in an axis direction, and a vertical cross-sectional area of a gap space between an upper end of the fixed cup and a lower end of the motor rotor is larger than the vertical cross-sectional area of the penetrating flow passage.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013251309A JP5984787B2 (en) | 2013-12-04 | 2013-12-04 | Scroll compressor |
JP2013-251309 | 2013-12-04 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20150152864A1 true US20150152864A1 (en) | 2015-06-04 |
Family
ID=53163861
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/527,071 Abandoned US20150152864A1 (en) | 2013-12-04 | 2014-10-29 | Scroll compressor |
Country Status (5)
Country | Link |
---|---|
US (1) | US20150152864A1 (en) |
JP (1) | JP5984787B2 (en) |
KR (1) | KR101658711B1 (en) |
CN (2) | CN204327493U (en) |
TW (2) | TWI575160B (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3315777A4 (en) * | 2015-11-05 | 2018-08-22 | Mitsubishi Heavy Industries Thermal Systems, Ltd. | Scroll compressor and method for producing scroll compressor |
EP3508726A1 (en) * | 2018-01-04 | 2019-07-10 | LG Electronics Inc. | Motor operated compressor |
FR3102812A1 (en) * | 2019-11-06 | 2021-05-07 | Danfoss Commercial Compressors | Scroll compressor with a force-mounted motor and a vertically central suction inlet |
US11187231B2 (en) * | 2018-09-28 | 2021-11-30 | Samsung Electronic Co., Ltd. | Scroll compressor |
US11624364B2 (en) * | 2019-08-30 | 2023-04-11 | Kabushiki Kaisha Toyota Jidoshokki | Electric compressor |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
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JP5984787B2 (en) * | 2013-12-04 | 2016-09-06 | 三菱電機株式会社 | Scroll compressor |
JP6858606B2 (en) * | 2017-03-21 | 2021-04-14 | 日立ジョンソンコントロールズ空調株式会社 | Sealed electric compressor |
CN106968948A (en) * | 2017-04-28 | 2017-07-21 | 上海海立新能源技术有限公司 | A kind of compressor |
CN116838604A (en) | 2022-03-23 | 2023-10-03 | 日立江森自控空调有限公司 | compressor |
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Also Published As
Publication number | Publication date |
---|---|
TWI637111B (en) | 2018-10-01 |
CN104696225B (en) | 2017-08-08 |
JP2015108334A (en) | 2015-06-11 |
CN204327493U (en) | 2015-05-13 |
TW201713855A (en) | 2017-04-16 |
JP5984787B2 (en) | 2016-09-06 |
TWI575160B (en) | 2017-03-21 |
KR101658711B1 (en) | 2016-09-21 |
KR20150065148A (en) | 2015-06-12 |
TW201540956A (en) | 2015-11-01 |
CN104696225A (en) | 2015-06-10 |
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