EP2610491A1 - Hermetically sealed compressor - Google Patents
Hermetically sealed compressor Download PDFInfo
- Publication number
- EP2610491A1 EP2610491A1 EP11819557.7A EP11819557A EP2610491A1 EP 2610491 A1 EP2610491 A1 EP 2610491A1 EP 11819557 A EP11819557 A EP 11819557A EP 2610491 A1 EP2610491 A1 EP 2610491A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotor
- rotational axis
- swirl flow
- balance weight
- space
- 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.)
- Withdrawn
Links
- 238000004891 communication Methods 0.000 claims abstract description 63
- 230000006835 compression Effects 0.000 claims abstract description 31
- 238000007906 compression Methods 0.000 claims abstract description 31
- 239000012530 fluid Substances 0.000 claims abstract description 27
- 238000006073 displacement reaction Methods 0.000 claims description 31
- 239000000463 material Substances 0.000 claims description 10
- 239000002245 particle Substances 0.000 claims description 8
- 238000007599 discharging Methods 0.000 claims description 4
- 239000000470 constituent Substances 0.000 claims description 2
- 230000005484 gravity Effects 0.000 claims description 2
- 239000003507 refrigerant Substances 0.000 description 94
- 239000003921 oil Substances 0.000 description 81
- 238000012986 modification Methods 0.000 description 23
- 230000004048 modification Effects 0.000 description 23
- 230000002093 peripheral effect Effects 0.000 description 16
- 238000000926 separation method Methods 0.000 description 13
- 238000010586 diagram Methods 0.000 description 10
- 230000000694 effects Effects 0.000 description 10
- 229910000831 Steel Inorganic materials 0.000 description 6
- 239000010959 steel Substances 0.000 description 6
- 238000000034 method Methods 0.000 description 5
- 230000007423 decrease Effects 0.000 description 4
- 238000002474 experimental method Methods 0.000 description 3
- 238000005259 measurement Methods 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- 230000000052 comparative effect Effects 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 239000003595 mist Substances 0.000 description 2
- 229910001369 Brass Inorganic materials 0.000 description 1
- YCKRFDGAMUMZLT-UHFFFAOYSA-N Fluorine atom Chemical compound [F] YCKRFDGAMUMZLT-UHFFFAOYSA-N 0.000 description 1
- 239000010951 brass Substances 0.000 description 1
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 239000000835 fiber Substances 0.000 description 1
- 229910052731 fluorine Inorganic materials 0.000 description 1
- 239000011737 fluorine Substances 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 239000012212 insulator Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 239000010721 machine oil Substances 0.000 description 1
- 238000005070 sampling Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 210000002268 wool Anatomy 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/026—Lubricant separation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C29/045—Heating; Cooling; Heat insulation of the electric motor in hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/807—Balance weight, counterweight
-
- 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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
Definitions
- the present invention relates to a hermetic compressor, and more specifically to a technique for separating lubricating oil from a compressed working fluid.
- FIG. 25 shows an overview of a compressor described in Patent Literature 1.
- a motor including a rotor 211 and a stator 213 is disposed in a closed casing 203 of the compressor.
- a compression mechanism (not shown) is disposed below the motor.
- a refrigerant compressed in the compression mechanism is discharged into the internal space of the closed casing 203.
- An oil separation plate 237 that rotates together with the rotor 211 is provided at the end of the rotor 211. The oil separation plate 237 applies a centrifugal force to a multiphase flow of the compressed refrigerant and oil.
- the oil separation plate 237 has an approximately disk shape. Projections 239 and recesses 245 are formed radially on the bottom surface of the oil separation plate 237. The projections 239 and the recesses 245 each extend continuously to the outer periphery of the oil separation plate 237. The flow of the refrigerant containing oil particles travels along the projections 239, is scattered by the centrifugal force from the end of each projection 239, and collides with the inner peripheral surface of the rotor 213. Thus, the oil is separated from the refrigerant. The refrigerant is discharged outside the closed casing 203 through a discharge pipe 235.
- Patent Literature 2 discloses a method of causing a compressed refrigerant to pass through an insulator so as to promote the separation of oil from the refrigerant.
- the separated oil returns to an oil reservoir in the bottom portion of the closed casing through a gap between the rotor and the stator or through a gap between the stator and the closed casing.
- the present invention provides a hermetic compressor including: a closed casing having an oil reservoir in its bottom portion; a compression mechanism, disposed in the closed casing, for compressing a working fluid; a motor, disposed above the compression mechanism in the closed casing, for driving the compression mechanism, the motor having a rotor and a stator; an upper space, formed above the motor, as a part of an internal space of the closed casing; a lower space, formed between the motor and the compression mechanism, as a part of the internal space of the closed casing; a discharge pipe opening into the upper space, for discharging the compressed working fluid outside the hermetic compressor; a first balance weight protruding from an upper surface of the rotor toward the upper space; a swirl flow generating portion protruding from the upper surface of the rotor toward the upper space, the swirl flow generating portion being disposed at a position closer to a rotational axis of the motor than the first balance weight; a second balance weight protruding from a lower surface of the
- a three-dimensional annular trajectory of the first balance weight formed around the rotational axis when the motor is driven is defined as a first trajectory
- a plane obtained by cutting the first trajectory with a first plane parallel to the rotational axis and including the rotational axis is defined as a first cross section
- a three-dimensional annular trajectory of the second balance weight formed around the rotational axis when the motor is driven is defined as a second trajectory
- a plane obtained by cutting the second trajectory with a second plane parallel to the rotational axis and including the rotational axis is defined as a second cross section
- a three-dimensional annular trajectory of the swirl flow generating portion formed around the rotational axis when the motor is driven is defined as a third trajectory
- a plane obtained by cutting the third trajectory with a third plane parallel to the rotational axis and including the rotational axis is defined as a third cross section, an area of a micro-region included in a specific region on an arbitrary plane parallel to the rotational axis and
- the hermetic compressor further includes a discharge direction deflecting portion for causing the compressed working fluid to travel from the communication passage to the upper space, while deflecting the working fluid in a direction inclined with respect to a direction parallel to the rotational axis.
- the sum of the second moment of area of the first cross section and the second moment of area of the third cross section is greater than the second moment of area of the second cross section. That is, the swirl flow in the upper space is stronger and the swirl flow in the lower space is weaker. This promotes the effect of separating the oil from the working fluid by a centrifugal force in the upper space. Furthermore, the return of the oil from the upper space to the oil reservoir can be facilitated by increasing the swirl flow in the upper space and reducing the swirl flow in the lower space relatively. This can prevent lubrication failure from occurring in the compression mechanism due to a drop in the oil level. Moreover, since the stability of the oil level is enhanced by reducing the swirl flow in the lower space, splashing of the oil can also be reduced.
- the discharge direction deflecting portion since the discharge direction deflecting portion is provided, the compressed working fluid travels from the communication passages to the upper space, while being deflected in a direction inclined with respect to a direction parallel to the rotational axis. This allows the swirl flow of the working fluid to be generated at a position closer to the outlet of the communication passage in the direction parallel to the rotational axis of the motor. As a result, the flow distance of the working fluid in the upper space can be increased, which can reduce the discharge of the oil from the compressor.
- a rotary compressor 100 of the present embodiment includes a closed casing 2, a compression mechanism 4, and a motor 6.
- the compression mechanism 4 and the motor 6 are disposed in one closed casing 2. That is, the rotary compressor 100 is configured as a hermetic compressor.
- the motor 6 is located above the compression mechanism 4.
- the closed casing 2 has an oil reservoir 3 formed in its bottom portion.
- the compression mechanism 4 is immersed in oil (refrigerating machine oil) held in the oil reservoir 3.
- the compression mechanism 4 is coupled to the motor 6 by a shaft 9 so as to be driven by the motor 6.
- Alower space 5 and an upper space 7 are formed in the closed casing 2.
- the lower space 5 is a space formed between the compression mechanism 4 and the motor 6 in the axial direction of the shaft 9.
- the upper space 7 is a space formed above the motor 6.
- the longitudinal direction of the shaft 9 is parallel to the vertical direction. That is, the rotary compressor 100 is a vertical rotary compressor.
- the compression mechanism 4 has an upper bearing 12, a piston 10, a cylinder 11, and a lower bearing 13.
- the piston 10 is fitted to an eccentric portion 9a of the shaft 9 within the cylinder 11.
- a compression chamber 11c having a crescent shape in plan view is formed between the outer peripheral surface of the piston 10 and the inner peripheral surface of the cylinder 11.
- a torque generated in the motor 6 is transmitted to the piston 10 by the shaft 9.
- a refrigerant is compressed in the compression chamber 11c.
- the type of the refrigerant as a working fluid is not particularly limited.
- a fluorine-containing refrigerant such as R410A or a natural refrigerant such as carbon dioxide can be used.
- the upper bearing 12 and the lower bearing 13 are mounted on the top and the bottom of the cylinder 11, respectively.
- the shaft 9 is rotatably supported by the upper bearing 12 and the lower bearing 13.
- a discharge muffler 24 having a discharge port 25 is provided on the top of the upper bearing 12.
- the compressed refrigerant travels from the compression mechanism 4 to the lower space 5 through the interior of the discharge muffler 24 and the discharge port 25.
- An oil passage 26 for returning the oil separated from the refrigerant in the lower space 5 or the upper space 7 to the oil reservoir 3 is formed along the outer periphery of the upper bearing 12.
- a discharge pipe 8 for discharging the compressed refrigerant outside the closed casing 2 is provided in the top portion of the closed casing 2.
- a suction pipe 23 for introducing the refrigerant to be compressed into the compression mechanism 4 is provided in the side portion of the closed casing 2.
- the discharge pipe 8 penetrates the top portion of the closed casing 2 and opens into the upper space 7.
- the suction pipe 23 penetrates the side portion of the closed casing 2 and is inserted into the cylinder 11.
- the motor 6 includes a stator 14 and a rotor 15.
- the stator 14 is fixed to the inner wall of the closed casing 2.
- the stator 14 has an annular shape when viewed in the axial direction, and the rotor 15 is disposed within the stator 14.
- the rotor 15 is fixed to the shaft 9. Therefore, the rotational axis of the motor 6 coincides with the rotational axis O of the shaft 9.
- a small gap 16 (air gap) is formed between the inner peripheral surface of the stator 14 and the outer peripheral surface of the rotor 15 in the radial direction.
- a plurality of slit-shaped flow paths 17 extending in a direction parallel to the rotational axis O are formed between the outer peripheral surface of the stator 14 and the inner peripheral surface of the closed casing 2.
- the rotor 15 has a plurality of communication passages 20 communicating the lower space 5 and the upper space 7.
- the communication passages 20 are formed at equal angular intervals around the rotational axis O of the shaft 9, and each of them penetrates the rotor 15 in the direction parallel to the axial direction of the shaft 9.
- the refrigerant compressed in the compression mechanism 4 travels from the lower space 5 to the upper space 7 through the gap 16, the flow paths 17, or the communication passages 20.
- the oil separated from the refrigerant in the upper space 7 returns from the upper space 7 to the lower space 5 through the gap 16, the flow paths 17, or the communication passages 20.
- the rotor 15 has four communication passages 20, but the number of the communication passages 20 is not particularly limited.
- the rotor 15 has, as constituent elements of the rotor 15, a stack of steel plates 28, end plates 27 disposed on the top and the bottom of the stack of steel plates 28 to clamp the steel plates 28 therebetween and fix them together, and rivets (not shown).
- a first balance weight 18 and a second balance weight 19 are provided on the top and the bottom of the rotor 15, respectively.
- the balance weights 18 and 19 each have an arcuate shape, and surround the communication passages 20 in plan view.
- the second balance weight 19 is disposed symmetrically to the first balance weight 18 with respect to the rotational axis O of the shaft 9. That is, the second balance weight 19 is disposed at a position 180 degrees opposite to the position of the first balance weight 18 with respect to the rotational direction of the shaft 9.
- the second balance weight 19 is heavier than the first balance weight.
- the second balance weight 19 is located closer to the supporting point of the shaft 9 (the upper bearing 12 and the lower bearing 13) than the first balance weight 18. Therefore, the effect of preventing the whirling motion can be enhanced by making the second balance weight 19 relatively heavy.
- a swirl flow generating portion 21 is provided on the top of the rotor 15 to increase a swirl flow in the upper space 7.
- the swirl flow generating portion 21 protrudes from the upper surface of the rotor 15 toward the upper space 7 and is disposed at a position closer to the rotational axis O than the first balance weight 18.
- the swirl flow generating portion 21 includes a supporting ring 121 and baffle plates 122.
- the supporting ring 121 is a plate-like member, and is located closer to the rotational axis O than the communication passages 20 on the upper surface of the rotor 15.
- the baffle plates 122 have a flat plate shape and are formed integrally with the supporting ring 121 on the outer periphery of the supporting ring 121.
- Four baffle plates 122 are provided at equal angular intervals along the circumferential direction of the supporting ring 121.
- Each of the baffle plates 122 protrudes obliquely from the upper surface of the rotor 15 toward the upper space 7 (i.e., in a direction inclined with respect to a direction parallel to the rotational axis O of the motor 6).
- the swirl flow generating portion 21 has the same number of baffle plates 122 as the communication passages 20.
- the baffle plate 122 is provided at the outlet of the communication passage 20. Specifically, the baffle plate 122 is located in the rotational direction of the rotor 15 from the outlet of the communication passage 20. An image obtained by projecting the baffle plate 122 onto the upper surface of the rotor 15 overlaps the outlet of the communication passage 20. That is, the communication passage 20 is partially or entirely covered by the baffle plate 122.
- the baffle plate 122 serves as a discharge direction deflecting portion for deflecting the discharge direction of the refrigerant.
- the swirl flow generating portion 21 is also used as a discharge direction deflecting portion (baffle plate 122).
- the baffle plates 122 each are configured to direct the compressed refrigerant in a rotational direction opposite to that of the rotor 15 (hereinafter referred to as a "opposite rotational direction").
- This configuration can prevent the refrigerant in the upper space 7 and the refrigerant discharged from the communication passages 20 from colliding with each other at right angles. Therefore, the refrigerant discharged from the communication passages 20 can travel smoothly to the upper space 7. This means that the pressure loss at the outlet of the communication passage 20 is less likely to increase.
- the swirl flow generating portion 21 may have the baffle plate 122 at a position where it does not cover the outlet of the communication passage 20.
- the baffle plate 122 provided at such a position also has a function of increasing the swirl flow in the upper space 7, but does not have a function of deflecting the discharge direction of the refrigerant. Therefore, the flow distance of the refrigerant in the upper space 7 cannot be increased.
- the baffle plate 122 may be formed as a part of the end plate 27. Specifically, as shown in Fig. 4 , the baffle plate 122 can be formed by cutting and raising a part of the end plate 27 at a position covering the communication passage 20. In a configuration shown in Fig. 4 , the baffle plate 122 thus cut and raised serves as a swirl flow generating portion and a discharge direction deflecting portion.
- the shape of the discharge direction deflecting portion is not limited to a plate shape as long as it has a function of deflecting the discharge direction of the refrigerant.
- a swirl flow suppressing portion 22 is provided beneath the rotor 15 to reduce the swirl flow in the lower space 5.
- the swirl flow suppressing portion 22 is constituted by an annular cover 22 that completely covers the second balance weight 19.
- the second balance weight 19 is covered by the cover 22 to suppress the swirl flow in the lower space 5
- the pressure at the opening of the flow path 17 on the lower space 5 side drops.
- the oil separated in the upper space 7 can be returned smoothly to the lower space 5 and the oil reservoir 3 through the flow path 17.
- splashing of oil in the oil reservoir 3 can be reduced.
- the first balance weight 18, the second balance weight 19, the swirl flow generating portion 21 and the swirl flow suppressing portion 22 are designed to increase the swirl flow in the upper space 7 and reduce the swirl flow in the lower space 5.
- One of the factors in the generation of swirl flows in the lower space 5 and the upper space 7 is that the refrigerant filled in the lower space 5 and the upper space 7 is subjected to the displacement action of the first balance weight 18, the second balance weight 19, and the swirl flow generating portion 21.
- a three-dimensional annular trajectory of the first balance weight 18 formed around the rotational axis O when the motor 6 is driven is defined as a first trajectory
- a plane obtained by cutting the first trajectory with a first plane parallel to the rotational axis O and including the rotational axis O is defined as a first cross section 33.
- the first cross section 33 can also be defined as follows.
- a plane that is a part of the surface of the first balance weight 18 and applies displacement action to the refrigerant when the motor 6 is driven is defined as a first displacement surface 18p
- an image obtained by projecting the first displacement surface 18p onto the first plane parallel to the rotational axis O and including the rotational axis O is defined as a first projected image.
- the first projected image can have various shapes and areas because the first plane can be determined without limitation, but herein the first plane is determined so that the area of the first projected image has a maximum value. In this case, the first projected image coincides with the first cross section 33.
- a second cross section 34, a second displacement surface 19p, a second plane, and a second projected image can be defined according to the same criteria as applied to the first balance weight 18.
- a third cross section 35, a third displacement surface, a third plane, and a third projected image can be defined according to the same criteria as applied to the first balance weight 18.
- a three-dimensional annular trajectory of the swirl flow generating portion 21 formed around the rotational axis O when the motor 6 is driven is defined as a third trajectory
- a plane obtained by cutting the third trajectory with a third plane parallel to the rotational axis O and including the rotational axis O is defined as a third cross section 35.
- four baffle plates 122 for applying displacement action to the refrigerant are provided. Therefore, the third cross section 35 is composed of four cross sections having the same shape.
- the third cross section 35 also can be defined as follows.
- a plane that is a part of the surface of the swirl flow generating portion 21 and applies displacement action to the refrigerant when the motor 6 is driven is defined as a third displacement surface 21p
- an image obtained by projecting the third displacement surface 21p onto the third plane parallel to the rotational axis O and including the rotational axis O is defined as a third projected image.
- the surface of the baffle plate 122 forms the third displacement surface 21p.
- the third projected image can have various shapes and areas because the third plane can be determined without limitation, but herein the third plane is determined so that the area of the third projected image has a maximum value. In this case, the third projected image coincides with the third cross section 35.
- the area of a micro-region 136 included in a specific region 135 on an arbitrary plane parallel to the rotational axis O and including the rotational axis O is defined as dA
- the distance from the rotational axis O to the centroid of the micro-region 136 is defined as r
- the length of the micro-region 136 in a radial direction is defined as dr
- the height of the micro-region 136 in a direction parallel to the rotational axis O is defined as dh
- the value M A represented by the following equation (1) is defined as a second moment of area.
- the micro-region 136 is rectangular.
- the second moment of area of the first cross section 33 is defined as a 1st second moment of area M A1 .
- the second moment of area of the second cross section 34 is defined as a 2nd second moment of area M A2 .
- the second moment of area of the third cross section 35 is defined as a 3rd second moment of area M A3 .
- the 1st to 3rd second moments of area can be calculated using Equation (1) for the first cross section 33, the second cross section 34, and the third cross section 35, respectively.
- the first balance weight 18, the second balance weight 19, and the swirl flow generating portion 21 are designed so that the relationship among these 1st to 3rd second moments of area satisfies the following equation (2).
- the "second moment of area of the first cross section 33" means a second moment of area calculated using Equation (1) for the first cross section 33. This also applies to the second cross section 34 and the third cross section 35.
- the swirl flow generating portion 21 has a plurality of baffle plates 122. Therefore, the second term in the left-hand side of Equation (2) is represented as a sum of a plurality of 3rd second moments of area of the plurality of baffle plates 122. In the case where a plurality of first balance weights 18 are provided, the first term in the left-hand side of Equation (2) is represented as a sum of a plurality of 1st second moments of area of the plurality of first balance weights 18. Likewise, in the case where a plurality of second balance weights 19 are provided, the right-hand side of Equation (2) is represented as a sum of a plurality of 2nd second moments of area of the plurality of second balance weights 19.
- the second balance weight 19 is covered by a cover 22 to reduce the area of the second displacement surface 19p of the second balance weight 19.
- the second displacement surface 19p displaces the refrigerant.
- the area of the second displacement surface 19p is substantially zero, if the presence of screws or the like for fixing the cover 22 to the rotor 15 is ignored. Therefore, the right-hand side of Equation (2) is zero and thus the relationship of Equation (2) is satisfied.
- the 1st second moment of area M A1 is equal to the second moment of area of the first projected image on the first plane, when the first plane is determined so that the area of the first projected image has a maximum value.
- the 2nd second moment of area M A2 is equal to the second moment of area of the second projected image on the second plane, when the second plane is determined so that the area of the second projected image has a maximum value.
- the 3rd second moment of area M A3 is equal to the second moment of area of the third projected image on the third plane, when the third plane is determined so that the area of the third projected image has a maximum value.
- Fig. 9 the flow of the refrigerant in the lower space 5, the flow of the refrigerant in the upper space 7, and the flow of the oil returning from the upper space 7 to the oil reservoir 3 are indicated by an arrow 38a, an arrow 38b, and a dashed arrow 39, respectively.
- the oil held in the oil reservoir 3 is used for lubrication and sealing of the sliding parts of the compression mechanism 4.
- the compressed refrigerant containing oil particles (oil mist) is discharged from the compression mechanism 4 to the lower space 5 in a high-temperature and high-pressure state.
- a swirl flow field is formed by the rotation of the rotor 15, but the intensity of the flow is reduced by the function of the cover 22, compared to that in the upper space 7.
- the refrigerant discharged into the lower space 5 is introduced from the lower space 5 to the upper space 7 through the communication passages 20.
- the refrigerant discharged into the upper space 7 is deflected in the swirling direction and the outer peripheral direction by centrifugal forces generated by the baffle plates 122 serving also as the swirl flow generating portion 21 and the first balance weight 18 as well as a flow deflecting action performed by the baffle plates 122 serving also as the swirl flow generating portion 21.
- the oil particles are separated from the refrigerant by the centrifugal forces during travelling. Then, the refrigerant is discharged outside the closed casing 2 through the discharge pipe 8. The oil separated by the centrifugal forces in the upper space 7 adheres to the inner peripheral surface of the stator 14 or the inner wall of the closed casing 2. Then, the oil returns to the oil reservoir 3 through the air gap 16 or the flow path 17.
- a flow field generated by a swirl flow is described.
- a model is assumed, in which a rotor 37a is placed in a cylindrical container 37 and the rotor 37a is rotating about the central axis O 1 of the cylindrical container 37, as shown in Fig. 10 .
- a pressure field 37b is generated with a low pressure near the central axis O 1 and a high pressure near the inner peripheral surface of the cylindrical container 37. This is the result of the effect of directing the flow radially outwardly by the centrifugal force of the flow itself and the effect of converting kinetic energy produced by swirling into pressure energy near the inner peripheral surface of the cylindrical container 37.
- a pressure field 37c indicated by a dashed line is generated. That is, the increase in the intensity of swirling increases the centrifugal force of the swirl flow itself. Therefore, the pressure field 37c tends to have an even lower pressure near the central axis O 1 of the cylindrical container 37.
- kinetic energy produced by swirling with the inclusion of additional kinetic energy is converted into pressure energy near the inner peripheral surface of the cylindrical container 37. Therefore, the pressure field 37c tends to have an even higher pressure near the inner peripheral surface of the cylindrical container 37.
- the second balance weight 19 is heavier than the first balance weight 18.
- the balance weights 18 and 19 are made of a metal such as brass.
- the volume of the second balance weight 19 must be greater than that of the first balance weight 18 to make the second balance weight 19 heavier than the first balance weight 18.
- the area of the displacement surface 19p of the second balance weight 19 exceeds the area of the displacement surface 18 of the first balance weight 18.
- a rotary compressor 100g shown in Fig. 11 does not have components corresponding to the swirl flow generating portion (baffle plate 122) and the swirl flow suppressing portion (cover 22) in the rotary compressor 100 of the present embodiment. Except for these components, the configuration of the rotary compressor 100g is the same as that of the rotary compressor 100 of the present embodiment. That is, a first balance weight 18g and a second balance weight 19g are each fixed to a rotor 15g and rotate with the rotor 15g. The second balance weight 19g has a larger displacement area than the first balance weight 18g. Therefore, the swirl flow formed by the second balance weight 19g in a lower space 5g is stronger than that formed by the first balance weight 18g in an upper space 7g.
- the oil separated by a centrifugal force in the upper space 7g reaches the inner wall of the closed casing 2g in the upper space 7g, and then returns to an oil reservoir 3g by its own weight through the flow path 17g.
- the pressure in the opening of the flow path 17g on the lower space 5g side is excessively higher than that in the opening of the flow path 17g on the upper space 7g side, such a high pressure makes it difficult for the oil to return smoothly through the flow path 17g.
- the refrigerant travels from the lower space 5g to the upper space 7g mainly through the flow path 17g, the flow of the oil from the upper space 7g to the lower space 5g (indicated by a dashed arrow 139) is impeded. As a result, the oil is likely to accumulate near the inner wall of the closed casing 2g in the upper space 7g. The accumulated oil is again mixed with the refrigerant and discharged with the refrigerant outside the closed casing 2g.
- the swirl flow in the upper space 7 is increased by the function of the swirl flow generating portion 21 while the swirl flow in the loser space 5 is suppressed by the function of the swirl flow suppressing portion 22. Therefore, as indicated by a solid line 140a in Fig. 12 , the pressure in the opening of the flow path 17 on the upper space 7 side is higher than that in the opening of the flow path 17 on the lower space 5 side, or the difference between the pressure in the opening of the flow path 17 on the upper space 7 side and that in the opening of the flow path 17 on the lower space 5 side is relatively small.
- the pressure near the center of the rotor 15 decreases when the swirl flow is increased, while it increases when the swirl flow is suppressed.
- the swirl flow generating portion 21 is provided in the upper space 7 and the swirl flow suppressing portion 22 is provided in the lower space 5
- the pressure near the center of the rotor 15 becomes lower in the upper space 7 and higher in the lower space 5.
- the amount of refrigerant flowing from the lower space 5 to the upper space 7 through the communication passage 20 increases, and the refrigerant can be prevented from flowing from the upper space 7 to the lower space 5 through the flow path 17, or the amount of refrigerant flowing from the lower space 5 to the upper space 7 through the flow path 17 decreases significantly.
- the amount of refrigerant flowing from the compression mechanism 4 to the discharge pipe 8 through the flow path 17 decreases, the oil can be returned from the upper space 7 to the oil reservoir 3 smoothly through the flow path 17.
- Equation (3) p is the density of a fluid
- V is the rotational speed of a rotor
- ⁇ is the angular velocity of the rotor
- r is the turning radius of a displacement portion (displacement surface) of the rotor
- A is the projected area of the displacement portion (displacement surface) of the rotor.
- Equation (3) assuming that the rotational speed V of the rotor is far below 0.3 times the sound velocity in a refrigerant flow, the refrigerant can be regarded as an incompressible fluid.
- the density p is constant.
- the angular velocity ⁇ also is constant under the same operating conditions.
- the swirl momentum Kr that contributes to the intensity of the swirl flow applied to the flow field is proportional to a value obtained by multiplying the square of the turning radius r by the projected area A.
- the value obtained by multiplying the square of the turning radius r by the projected area A corresponds to the second moment of area described above. That is, the second moment of area represents the intensity of swirling applied to the refrigerant flow.
- a balance weight 18g is provided on the top of a rotor 15g (in the compressor 100g shown in Fig. 11 ), as shown in Fig. 13A and Fig. 13B , is described.
- the rotational direction of the rotor 15g is considered as a static system.
- a refrigerant flow 42g discharged from a communication passage 20g to an upper space 7g collides with a refrigerant flow 41g in the upper space 7g at an almost right angle. In this case, a large pressure loss may occur.
- baffle plates 21g are disposed at the outlets of the communication passages 20g, as shown in Fig. 14A and Fig. 14B , is described.
- Each of the baffle plates 21g is located in the rotational direction of the rotor 15g with respect to the outlet of the communication passage 20g.
- the baffle plate 21g extends straight in a direction parallel to the rotational axis O, and thus does not cover the outlet of the communication passage 20g.
- Such a baffle plate 21g can prevent the refrigerant flow 42g from colliding with the refrigerant flow 41g at a right angle. This means that the pressure loss at the outlet of the communication passage 20 can be reduced.
- the baffle plate 21g has no ability to deflect the refrigerant flow. Therefore, as shown in Fig. 17 , the refrigerant tends to flow upward in the vertical direction.
- baffle plates 122 are disposed to cover the outlets of the communication passages 20, as shown in Fig. 15A and Fig. 15B .
- a refrigerant flow 42 discharged from the communication passage 20 to the upper space 7 is subjected to the deflecting action of the baffle plate 122, the refrigerant is discharged in the opposite rotational direction of the rotor 15. That is, the refrigerant travels from the communication passages 20 to the upper space 7, while being deflected in a direction inclined with respect to the direction parallel to the rotational axis O.
- a swirl flow begins to be formed at a position relatively close to the upper surface of the rotor 15.
- the flow distance (time) of the refrigerant in the upper space 7 increases, which can promote the centrifugal separation of oil.
- the baffle plate 122 may completely cover the outlet of the communication passage 20 in plan view, or may partially cover it. That is, a projected image obtained by projecting the baffle plate 122 onto the upper surface of the rotor 15 may contain the opening area of the communication passage 20, or the projected image of the baffle plate 122 may overlap the opening area. For example, experimental results under high load conditions (a high rotational speed and a high pressure ratio) show that an excellent effect is obtained when the baffle plate 122 covers about 85% of the opening area.
- Fig. 18 is a graph showing the results of experiments conducted to ascertain the effect of the rotary compressor 100 of the present embodiment.
- the vertical axis represents the amount of discharged oil.
- the experiments were conducted under high load conditions, and the amount of oil discharged with the refrigerant through the discharge pipe was measured. The amount of the discharged oil was evaluated by sampling the refrigerant at the outlet of a condenser in a refrigeration cycle.
- "Embodiment” shows the measurement result in the rotary compressor described with reference to Fig. 1 , etc.
- “Comparative Example” shows the measurement result in a rotary compressor in which the swirl flow generating portion 21 and the swirl flow suppressing portion 22 (cover) of the rotary compressor of the embodiment are removed.
- First Modification shows the measurement result in a rotary compressor according to a first modification described later.
- the amount of oil discharged from the rotary compressor of the present embodiment was small, i.e., "0.44", when the amount of oil discharged from the rotary compressor of Comparative Example was "1".
- the amount of oil discharged from the rotary compressor of the first modification described later was even smaller, i.e., "0.1".
- the inlet of the discharge pipe 8 is located near the upper surface of the rotor 15. More specifically, the lower end of the discharge pipe 8 is located below the upper end of the stator 14 in the direction parallel to the rotational axis O of the shaft 9 (i.e., the vertical direction).
- the rotational axis O of the shaft 9 passes through the inlet of the discharge pipe 8. More specifically, the rotational axis O of the shaft 9 coincides with the center of the inlet of the discharge pipe 8.
- a refrigerant is discharged from the communication passage 20 to the upper space 7, and then travels, while swirling and being deflected, toward the inner wall of the closed casing 2 by the centrifugal force and the action of the baffle plates 122. Then, the refrigerant goes downward along the outer peripheral surface of the discharge pipe 8 while swirling and enters the discharge pipe 8. Since the flow distance (time) of the refrigerant flow in the upper space 7 can be increased, the separation of oil can further be promoted. Furthermore, since the refrigerant forms a downflow immediately before it enters the discharge pipe 8, the oil separation by the weight of the refrigerant itself also can be promoted. As a result, as shown in Fig. 18 , the amount of discharged oil can further be reduced.
- a space filling member 22b is used instead of the cover 22 as a swirl flow suppressing portion.
- the space filling member 22b has a smaller specific gravity than the second balance weight 19, and is provided along the rotational trajectory of the second balance weight 19. That is, the space filling member 22b is disposed symmetrically to the second balance weight 19 with respect to a plane including the rotational axis O, and fills the space along the trajectory of the second balance weight 19.
- the area of the displacement surface of the second balance weight 19 can be reduced by the space filling member 22b, like the cover 22 described with reference to Fig. 1 , etc.
- the space filling member 22b is made of a material having voids into which the refrigerant containing oil particles can penetrate.
- the space filling member 22b can be made of a material having voids, such as foamed materials, metal fiber woven materials, and steel wool. Since these materials are relatively light in weight, the function of the second balance weight 19 as a balance weight is less likely to be impaired.
- the shape of the space filling member 22b is not particularly limited as long as the area of the displacement surface of the second balance weight 19 can be reduced. In the modification shown in Fig. 20 , the shape of the space filling member 22b is determined so that the area of the displacement surface of the second balance weight 19 is substantially zero. The area of the displacement surface of the space filling member 22b also is zero. That is, a combination of the second balance weight 19 and the space filling member 22b forms an annular shape.
- the refrigerant flow around the second balance weight 19 contains oil particles.
- the space filling member 22b is fixed to the rotor 15, and rotates with the rotor 15. Therefore, a shear flow is formed between the space filling member 22b and the refrigerant flow.
- the space filling member 22b is made of a material having voids such as a foamed material, oil particles enter the foamed material due to turbulence in the refrigerant flow, etc. Thereby, the space filling member 22b serves as an oil mist trap.
- a discharge port 25 for discharging the refrigerant compressed in the compression mechanism 4 to the lower space 5 may be formed at a position where it overlaps the second balance weight 19 and the space filling member 22b, that is, a position where the discharge port 25 overlaps the rotational trajectory of the second balance weight 19, in the direction parallel to the rotational axis O (i.e., in the vertical direction).
- the discharge port 25, the second balance weight 19, and the space filling member 22b are projected on a plane perpendicular to the rotational axis O, the projected image of the discharge port 25 may overlap the projected image of the second balance weight 19 and/or the projected image of the space filling member 22b.
- the refrigerant discharged to the lower space 5 through the discharge port 25 can collide directly with the space filling member 22b.
- the amount of oil particles entering the voids in the space filling member 22b increase, and the oil separation effect of the space filling member 22b can be sufficiently obtained.
- a cover 22c as a swirl flow suppressing portion may be formed integrally with the end plate for clamping and fixing the stack of steel plates 28 constituting the rotor 15. Thereby, the number of components can be reduced.
- the cover 22c has an annular shape in plan view.
- a plurality of through-holes 44 are each formed at a position corresponding to the inlet of the communication passage 20. The refrigerant can move from the lower space 5 to the communication passages 20 through the through-holes 44 and the interior of the cover 22c.
- a swirl flow generating portion 146 shown in Fig. 23 has an end plate 27 and a first balance weight 18 integrated with the end plate 27. That is, the end plate 27 and the first balance weight 18 are formed as a single component by a casting method or the like. This can reduce the number of components and simplify the assembly process of the compressor.
- the end plate 27 is caulked and fixed to the stack of steel plates 28 to form the rotor 15.
- the communication passages 20 of the rotor 15 are covered by roof portions 46 provided on the end plate 27.
- the roof portion 46 constitutes a discharge direction deflecting portion.
- One roof portion 46 is provided for one communication passage 20.
- the roof portion 46 has walls above the outlet of the communication passage 20, downstream thereof in the rotational direction of the rotor 15, on the radially inner peripheral side, and on the radially outer peripheral side.
- the roof portion 46 has the shape of a small box with an opening only in the opposite rotational direction of the rotor 15.
- the refrigerant is discharged from the communication passage 20 in the opposite rotational direction of the rotor 15 by the function of the roof portions 46.
- an outlet part 48 of the communication passage 20 extends in a direction inclined with respect to the direction parallel to the rotational axis O of the motor 6.
- the compressed refrigerant travels from the communication passage 20 to the upper space 7, while being deflected in a direction that is opposite to the rotational direction of the rotor 15 and is inclined with respect to the direction parallel to the rotational axis O. That is, the discharge direction deflecting portion is constituted by the outlet part 48.
- a refrigerant flow 42 from the communication passage 20 does not collide with a refrigerant flow 41 at a right angle in the upper space 7. Therefore, an increase in the pressure loss at the outlet of the communication passage 20 can be prevented.
- Fig. 24A does not indicate a swirl flow generating portion for increasing a swirl flow.
- the swirl flow generating portion (for example, the baffle plate 122 shown in Fig. 3 ) may be provided at a position where it does not cover the outlet of the communication passage 20.
- a baffle plate 122 protruding obliquely from the upper surface of the rotor 15 so as to extend in the same direction as the outlet part 48 is provided as a swirl flow generating portion.
- both the outlet part 48 and the baffle plate 122 have the function as a discharge direction deflecting portion.
- This configuration ensures that a refrigerant flow from the communication passage 20 is directed toward the opposite rotational direction of the rotor 15.
- This configuration has the potential to further reduce the pressure loss that occurs when the refrigerant flow 42 is deflected.
- the configurations of the first to sixth modifications can be arbitrarily combined in the rotary compressor 100 shown in Fig. 1 , without departing from the spirit and scope of the present invention.
- the present invention is not limited to a rotary compressor, and can be applied to other hermetic compressors.
- the hermetic compressor of the present invention is suitably applicable to refrigeration cycle apparatuses used for air conditioners, water heaters, etc. Since the flow of oil into a condenser and an evaporator of a refrigeration cycle apparatus can be reduced, the heat exchange efficiency of the condenser and the evaporator can be improved.
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Abstract
A hermetic compressor (100) includes a closed casing (2), a compression mechanism (4), a motor (6), a discharge pipe (8), a first balance weight (18), a swirl flow generating portion (21), and a second balance weight (19). The motor (6) has a stator (14) and a rotor (15). A communication passage (20) is formed in the rotor (15) so as to introduce, into an upper space (7), a working fluid compressed in the compression mechanism (4) and discharged to a lower space (5) of the closed casing (2). A baffle plate (122) is provided as a discharge direction deflecting portion for causing the compressed working fluid to travel from the communication passage (20) to the upper space (7), while deflecting the working fluid in a direction inclined with respect to a direction parallel to a rotational axis O. The baffle plate (122) may be constituted by a part of the swirl flow generating portion (21).
Description
- The present invention relates to a hermetic compressor, and more specifically to a technique for separating lubricating oil from a compressed working fluid.
- A known conventional example of an oil separation mechanism usable in a hermetic compressor is
Patent Literature 1.Fig. 25 shows an overview of a compressor described inPatent Literature 1. A motor including arotor 211 and astator 213 is disposed in a closedcasing 203 of the compressor. A compression mechanism (not shown) is disposed below the motor. A refrigerant compressed in the compression mechanism is discharged into the internal space of the closedcasing 203. Anoil separation plate 237 that rotates together with therotor 211 is provided at the end of therotor 211. Theoil separation plate 237 applies a centrifugal force to a multiphase flow of the compressed refrigerant and oil. - As shown in
Fig. 26A and Fig. 26B , theoil separation plate 237 has an approximately disk shape.Projections 239 andrecesses 245 are formed radially on the bottom surface of theoil separation plate 237. Theprojections 239 and therecesses 245 each extend continuously to the outer periphery of theoil separation plate 237. The flow of the refrigerant containing oil particles travels along theprojections 239, is scattered by the centrifugal force from the end of eachprojection 239, and collides with the inner peripheral surface of therotor 213. Thus, the oil is separated from the refrigerant. The refrigerant is discharged outside the closedcasing 203 through adischarge pipe 235. -
Patent Literature 2 discloses a method of causing a compressed refrigerant to pass through an insulator so as to promote the separation of oil from the refrigerant. - In the compressor described in
Patent Literature -
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Patent Literature 1JP 11(1999)-107967 A -
Patent Literature 2JP 2009-144581 A - With the techniques disclosed in
Patent Literatures - It is an object of the present invention to provide a hermetic compressor with less discharge of oil.
- The present invention provides a hermetic compressor including: a closed casing having an oil reservoir in its bottom portion; a compression mechanism, disposed in the closed casing, for compressing a working fluid; a motor, disposed above the compression mechanism in the closed casing, for driving the compression mechanism, the motor having a rotor and a stator; an upper space, formed above the motor, as a part of an internal space of the closed casing; a lower space, formed between the motor and the compression mechanism, as a part of the internal space of the closed casing; a discharge pipe opening into the upper space, for discharging the compressed working fluid outside the hermetic compressor; a first balance weight protruding from an upper surface of the rotor toward the upper space; a swirl flow generating portion protruding from the upper surface of the rotor toward the upper space, the swirl flow generating portion being disposed at a position closer to a rotational axis of the motor than the first balance weight; a second balance weight protruding from a lower surface of the rotor toward the lower space; and a communication passage formed in the rotor so as to introduce, into the upper space, the working fluid compressed in the compression mechanism and discharged to the lower space. When a three-dimensional annular trajectory of the first balance weight formed around the rotational axis when the motor is driven is defined as a first trajectory, a plane obtained by cutting the first trajectory with a first plane parallel to the rotational axis and including the rotational axis is defined as a first cross section, a three-dimensional annular trajectory of the second balance weight formed around the rotational axis when the motor is driven is defined as a second trajectory, a plane obtained by cutting the second trajectory with a second plane parallel to the rotational axis and including the rotational axis is defined as a second cross section, a three-dimensional annular trajectory of the swirl flow generating portion formed around the rotational axis when the motor is driven is defined as a third trajectory, a plane obtained by cutting the third trajectory with a third plane parallel to the rotational axis and including the rotational axis is defined as a third cross section, an area of a micro-region included in a specific region on an arbitrary plane parallel to the rotational axis and including the rotational axis is defined as dA, a distance from the rotational axis to a centroid of the micro-region is defined as r, and a value MA represented by the following equation (1) is defined as a second moment of area,
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- a sum of a second moment of area of the first cross section and a second moment of area of the third cross section is greater than a second moment of area of the second cross section. The hermetic compressor further includes a discharge direction deflecting portion for causing the compressed working fluid to travel from the communication passage to the upper space, while deflecting the working fluid in a direction inclined with respect to a direction parallel to the rotational axis.
- According to the present invention, the sum of the second moment of area of the first cross section and the second moment of area of the third cross section is greater than the second moment of area of the second cross section. That is, the swirl flow in the upper space is stronger and the swirl flow in the lower space is weaker. This promotes the effect of separating the oil from the working fluid by a centrifugal force in the upper space. Furthermore, the return of the oil from the upper space to the oil reservoir can be facilitated by increasing the swirl flow in the upper space and reducing the swirl flow in the lower space relatively. This can prevent lubrication failure from occurring in the compression mechanism due to a drop in the oil level. Moreover, since the stability of the oil level is enhanced by reducing the swirl flow in the lower space, splashing of the oil can also be reduced.
- Furthermore, since the discharge direction deflecting portion is provided, the compressed working fluid travels from the communication passages to the upper space, while being deflected in a direction inclined with respect to a direction parallel to the rotational axis. This allows the swirl flow of the working fluid to be generated at a position closer to the outlet of the communication passage in the direction parallel to the rotational axis of the motor. As a result, the flow distance of the working fluid in the upper space can be increased, which can reduce the discharge of the oil from the compressor.
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Fig. 1 is a cross-sectional view of a compressor according to an embodiment of the present invention. -
Fig. 2 is a perspective view of a rotor and balance weights. -
Fig. 3 is a perspective view of the rotor on which the balance weights and a swirl flow generating portion are provided. -
Fig. 4 is a perspective view of the rotor on which another swirl flow generating portion is provided. -
Fig. 5 is a perspective view of a swirl flow suppressing portion. -
Fig. 6A is a perspective view showing the definitions of a first cross section and a second cross section. -
Fig. 6B is a plan view showing the definitions of the first cross section and the second cross section. -
Fig. 7A is a perspective view showing the definition of a third cross section. -
Fig. 7B is a plan view showing the definition of the third cross section. -
Fig. 8 is a schematic diagram showing the definition of a second moment of area. -
Fig. 9 is a schematic diagram showing the flow of refrigerant and the flow of oil in the compressor. -
Fig. 10 is a schematic diagram showing a pressure field of a model in which a rotor is placed in a cylindrical container. -
Fig. 11 is a schematic diagram showing the flow of refrigerant and the flow of oil in a compressor without a swirl flow generating portion. -
Fig. 12 is a schematic diagram showing a pressure difference between two openings of a flow path. -
Fig. 13A is a perspective view of a rotor without a swirl flow generating portion. -
Fig. 13B is a schematic diagram showing a refrigerant flow in the vicinity of an outlet of a communication passage formed in the rotor shown inFig. 13A . -
Fig. 14A is a perspective view of a rotor with a swirl flow generating portion incapable of deflecting a refrigerant flow. -
Fig. 14B is a schematic diagram showing a refrigerant flow in the vicinity of an outlet of a communication passage formed in the rotor shown inFig. 14A . -
Fig. 15A is a perspective view of the rotor of the present embodiment. -
Fig. 15B is a schematic diagram showing a refrigerant flow in the vicinity of an outlet of a communication passage formed in the rotor ofFig. 15A . -
Fig. 16 is a schematic diagram showing a flow field in the upper space of the rotary compressor of the present embodiment. -
Fig. 17 is a schematic diagram showing a flow field in the upper space of a rotary compressor provided with the swirl flow generating portion shown inFig. 14A . -
Fig. 18 is a graph showing the results of experiments conducted to ascertain the effect of the rotary compressor of the present embodiment. -
Fig. 19 is a cross-sectional view of a compressor according to a first modification. -
Fig. 20 is a perspective view of a swirl flow suppressing portion according to a second modification. -
Fig. 21 is a cross-sectional view showing a preferred position of a discharge port. -
Fig. 22 is a perspective view of a swirl flow suppressing portion according to a third modification. -
Fig. 23 is a perspective view of a swirl flow generating portion according to a fourth modification. -
Fig. 24 Ais a schematic cross-sectional view of a discharge direction deflecting portion according to a fifth modification. -
Fig. 24B is a schematic cross-sectional view of a swirl flow generating portion and a discharge direction deflecting portion according to a sixth modification. -
Fig. 25 is a cross-sectional view of a conventional hermetic compressor. -
Fig. 26A is a bottom view of an oil separation plate provided in the conventional hermetic compressor. -
Fig. 26B is a cross-sectional view of the oil separation plate shown inFig. 26A , taken along the line B-B. - Hereinafter, the embodiments of the present invention will be described with reference to the drawings.
- As shown in
Fig. 1 , arotary compressor 100 of the present embodiment includes aclosed casing 2, acompression mechanism 4, and amotor 6. Thecompression mechanism 4 and themotor 6 are disposed in oneclosed casing 2. That is, therotary compressor 100 is configured as a hermetic compressor. In theclosed casing 2, themotor 6 is located above thecompression mechanism 4. Theclosed casing 2 has anoil reservoir 3 formed in its bottom portion. Thecompression mechanism 4 is immersed in oil (refrigerating machine oil) held in theoil reservoir 3. Thecompression mechanism 4 is coupled to themotor 6 by ashaft 9 so as to be driven by themotor 6.Alower space 5 and anupper space 7 are formed in theclosed casing 2. Thelower space 5 is a space formed between thecompression mechanism 4 and themotor 6 in the axial direction of theshaft 9. Theupper space 7 is a space formed above themotor 6. The longitudinal direction of theshaft 9 is parallel to the vertical direction. That is, therotary compressor 100 is a vertical rotary compressor. - The
compression mechanism 4 has anupper bearing 12, apiston 10, acylinder 11, and alower bearing 13. Thepiston 10 is fitted to aneccentric portion 9a of theshaft 9 within thecylinder 11. Acompression chamber 11c having a crescent shape in plan view is formed between the outer peripheral surface of thepiston 10 and the inner peripheral surface of thecylinder 11. A torque generated in themotor 6 is transmitted to thepiston 10 by theshaft 9. As thepiston 10 rotates within thecylinder 11, a refrigerant is compressed in thecompression chamber 11c. The type of the refrigerant as a working fluid is not particularly limited. A fluorine-containing refrigerant such as R410A or a natural refrigerant such as carbon dioxide can be used. - The
upper bearing 12 and thelower bearing 13 are mounted on the top and the bottom of thecylinder 11, respectively. Theshaft 9 is rotatably supported by theupper bearing 12 and thelower bearing 13. Adischarge muffler 24 having adischarge port 25 is provided on the top of theupper bearing 12. The compressed refrigerant travels from thecompression mechanism 4 to thelower space 5 through the interior of thedischarge muffler 24 and thedischarge port 25. Anoil passage 26 for returning the oil separated from the refrigerant in thelower space 5 or theupper space 7 to theoil reservoir 3 is formed along the outer periphery of theupper bearing 12. - A
discharge pipe 8 for discharging the compressed refrigerant outside theclosed casing 2 is provided in the top portion of theclosed casing 2. Asuction pipe 23 for introducing the refrigerant to be compressed into thecompression mechanism 4 is provided in the side portion of theclosed casing 2. Thedischarge pipe 8 penetrates the top portion of theclosed casing 2 and opens into theupper space 7. Thesuction pipe 23 penetrates the side portion of theclosed casing 2 and is inserted into thecylinder 11. - The
motor 6 includes astator 14 and arotor 15. Thestator 14 is fixed to the inner wall of theclosed casing 2. Thestator 14 has an annular shape when viewed in the axial direction, and therotor 15 is disposed within thestator 14. Therotor 15 is fixed to theshaft 9. Therefore, the rotational axis of themotor 6 coincides with the rotational axis O of theshaft 9. A small gap 16 (air gap) is formed between the inner peripheral surface of thestator 14 and the outer peripheral surface of therotor 15 in the radial direction. A plurality of slit-shapedflow paths 17 extending in a direction parallel to the rotational axis O are formed between the outer peripheral surface of thestator 14 and the inner peripheral surface of theclosed casing 2. - The
rotor 15 has a plurality ofcommunication passages 20 communicating thelower space 5 and theupper space 7. Thecommunication passages 20 are formed at equal angular intervals around the rotational axis O of theshaft 9, and each of them penetrates therotor 15 in the direction parallel to the axial direction of theshaft 9. The refrigerant compressed in thecompression mechanism 4 travels from thelower space 5 to theupper space 7 through thegap 16, theflow paths 17, or thecommunication passages 20. The oil separated from the refrigerant in theupper space 7 returns from theupper space 7 to thelower space 5 through thegap 16, theflow paths 17, or thecommunication passages 20. In the present embodiment, therotor 15 has fourcommunication passages 20, but the number of thecommunication passages 20 is not particularly limited. - As shown in
Fig. 2 , therotor 15 has, as constituent elements of therotor 15, a stack ofsteel plates 28,end plates 27 disposed on the top and the bottom of the stack ofsteel plates 28 to clamp thesteel plates 28 therebetween and fix them together, and rivets (not shown). In order to prevent whirling of therotor 15 during its rotation, afirst balance weight 18 and asecond balance weight 19 are provided on the top and the bottom of therotor 15, respectively. Thebalance weights communication passages 20 in plan view. Thesecond balance weight 19 is disposed symmetrically to thefirst balance weight 18 with respect to the rotational axis O of theshaft 9. That is, thesecond balance weight 19 is disposed at a position 180 degrees opposite to the position of thefirst balance weight 18 with respect to the rotational direction of theshaft 9. - The
second balance weight 19 is heavier than the first balance weight. Thesecond balance weight 19 is located closer to the supporting point of the shaft 9 (theupper bearing 12 and the lower bearing 13) than thefirst balance weight 18. Therefore, the effect of preventing the whirling motion can be enhanced by making thesecond balance weight 19 relatively heavy. - As shown in
Fig. 1 andFig. 3 , a swirlflow generating portion 21 is provided on the top of therotor 15 to increase a swirl flow in theupper space 7. The swirlflow generating portion 21 protrudes from the upper surface of therotor 15 toward theupper space 7 and is disposed at a position closer to the rotational axis O than thefirst balance weight 18. Specifically, the swirlflow generating portion 21 includes a supportingring 121 and baffleplates 122. The supportingring 121 is a plate-like member, and is located closer to the rotational axis O than thecommunication passages 20 on the upper surface of therotor 15. Thebaffle plates 122 have a flat plate shape and are formed integrally with the supportingring 121 on the outer periphery of the supportingring 121. Fourbaffle plates 122 are provided at equal angular intervals along the circumferential direction of the supportingring 121. Each of thebaffle plates 122 protrudes obliquely from the upper surface of therotor 15 toward the upper space 7 (i.e., in a direction inclined with respect to a direction parallel to the rotational axis O of the motor 6). In the present embodiment, the swirlflow generating portion 21 has the same number ofbaffle plates 122 as thecommunication passages 20. The protruding direction of eachbaffle plate 122 is set to, for example, 30 to 60 degrees, and typically 45 degrees, with respect to the direction perpendicular to the rotational axis O (i.e., a horizontal direction (= 0 degrees). - The
baffle plate 122 is provided at the outlet of thecommunication passage 20. Specifically, thebaffle plate 122 is located in the rotational direction of therotor 15 from the outlet of thecommunication passage 20. An image obtained by projecting thebaffle plate 122 onto the upper surface of therotor 15 overlaps the outlet of thecommunication passage 20. That is, thecommunication passage 20 is partially or entirely covered by thebaffle plate 122. By the function of thebaffle plate 122, the compressed refrigerant travels from thecommunication passage 20 to theupper space 7, while being deflected in the direction inclined with respect to the direction parallel to the rotational axis O. As described above, thebaffle plate 122 serves as a discharge direction deflecting portion for deflecting the discharge direction of the refrigerant. In the present embodiment, in order to suppress an increase in the number of components, the swirlflow generating portion 21 is also used as a discharge direction deflecting portion (baffle plate 122). - In the present embodiment, the
baffle plates 122 each are configured to direct the compressed refrigerant in a rotational direction opposite to that of the rotor 15 (hereinafter referred to as a "opposite rotational direction"). This configuration can prevent the refrigerant in theupper space 7 and the refrigerant discharged from thecommunication passages 20 from colliding with each other at right angles. Therefore, the refrigerant discharged from thecommunication passages 20 can travel smoothly to theupper space 7. This means that the pressure loss at the outlet of thecommunication passage 20 is less likely to increase. - The swirl
flow generating portion 21 may have thebaffle plate 122 at a position where it does not cover the outlet of thecommunication passage 20. Thebaffle plate 122 provided at such a position also has a function of increasing the swirl flow in theupper space 7, but does not have a function of deflecting the discharge direction of the refrigerant. Therefore, the flow distance of the refrigerant in theupper space 7 cannot be increased. - In order to further reduce the number of components, the
baffle plate 122 may be formed as a part of theend plate 27. Specifically, as shown inFig. 4 , thebaffle plate 122 can be formed by cutting and raising a part of theend plate 27 at a position covering thecommunication passage 20. In a configuration shown inFig. 4 , thebaffle plate 122 thus cut and raised serves as a swirl flow generating portion and a discharge direction deflecting portion. The shape of the discharge direction deflecting portion is not limited to a plate shape as long as it has a function of deflecting the discharge direction of the refrigerant. - As shown in
Fig. 1 andFig. 5 , a swirlflow suppressing portion 22 is provided beneath therotor 15 to reduce the swirl flow in thelower space 5. Specifically, the swirlflow suppressing portion 22 is constituted by anannular cover 22 that completely covers thesecond balance weight 19. When thesecond balance weight 19 is covered by thecover 22 to suppress the swirl flow in thelower space 5, the pressure at the opening of theflow path 17 on thelower space 5 side drops. Thereby, the oil separated in theupper space 7 can be returned smoothly to thelower space 5 and theoil reservoir 3 through theflow path 17. Furthermore, since the stability of the oil level is enhanced by suppressing the swirl flow in thelower space 5, splashing of oil in theoil reservoir 3 can be reduced. - In the present embodiment, the
first balance weight 18, thesecond balance weight 19, the swirlflow generating portion 21 and the swirlflow suppressing portion 22 are designed to increase the swirl flow in theupper space 7 and reduce the swirl flow in thelower space 5. One of the factors in the generation of swirl flows in thelower space 5 and theupper space 7 is that the refrigerant filled in thelower space 5 and theupper space 7 is subjected to the displacement action of thefirst balance weight 18, thesecond balance weight 19, and the swirlflow generating portion 21. - As shown in
Fig. 6A and Fig. 6B , a three-dimensional annular trajectory of thefirst balance weight 18 formed around the rotational axis O when themotor 6 is driven is defined as a first trajectory, and a plane obtained by cutting the first trajectory with a first plane parallel to the rotational axis O and including the rotational axis O is defined as afirst cross section 33. - The
first cross section 33 can also be defined as follows. A plane that is a part of the surface of thefirst balance weight 18 and applies displacement action to the refrigerant when themotor 6 is driven is defined as afirst displacement surface 18p, and an image obtained by projecting thefirst displacement surface 18p onto the first plane parallel to the rotational axis O and including the rotational axis O is defined as a first projected image. The first projected image can have various shapes and areas because the first plane can be determined without limitation, but herein the first plane is determined so that the area of the first projected image has a maximum value. In this case, the first projected image coincides with thefirst cross section 33. - For the
second balance weight 19, asecond cross section 34, asecond displacement surface 19p, a second plane, and a second projected image can be defined according to the same criteria as applied to thefirst balance weight 18. - Furthermore, for the swirl
flow generating portion 21, athird cross section 35, a third displacement surface, a third plane, and a third projected image can be defined according to the same criteria as applied to thefirst balance weight 18. Specifically, as shown inFig. 7A and Fig. 7B , a three-dimensional annular trajectory of the swirlflow generating portion 21 formed around the rotational axis O when themotor 6 is driven is defined as a third trajectory, and a plane obtained by cutting the third trajectory with a third plane parallel to the rotational axis O and including the rotational axis O is defined as athird cross section 35. In the present embodiment, fourbaffle plates 122 for applying displacement action to the refrigerant are provided. Therefore, thethird cross section 35 is composed of four cross sections having the same shape. - The
third cross section 35 also can be defined as follows. A plane that is a part of the surface of the swirlflow generating portion 21 and applies displacement action to the refrigerant when themotor 6 is driven is defined as athird displacement surface 21p, and an image obtained by projecting thethird displacement surface 21p onto the third plane parallel to the rotational axis O and including the rotational axis O is defined as a third projected image. In the present embodiment, the surface of thebaffle plate 122 forms thethird displacement surface 21p. The third projected image can have various shapes and areas because the third plane can be determined without limitation, but herein the third plane is determined so that the area of the third projected image has a maximum value. In this case, the third projected image coincides with thethird cross section 35. - Next, as shown in
Fig. 8 , the area of a micro-region 136 included in aspecific region 135 on an arbitrary plane parallel to the rotational axis O and including the rotational axis O is defined as dA, the distance from the rotational axis O to the centroid of themicro-region 136 is defined as r, the length of the micro-region 136 in a radial direction is defined as dr, the height of the micro-region 136 in a direction parallel to the rotational axis O is defined as dh, and the value MA represented by the following equation (1) is defined as a second moment of area. InFig. 8 , themicro-region 136 is rectangular. -
- Furthermore, the second moment of area of the
first cross section 33 is defined as a 1st second moment of area MA1. Likewise, the second moment of area of thesecond cross section 34 is defined as a 2nd second moment of area MA2. Likewise, the second moment of area of thethird cross section 35 is defined as a 3rd second moment of area MA3. The 1st to 3rd second moments of area can be calculated using Equation (1) for thefirst cross section 33, thesecond cross section 34, and thethird cross section 35, respectively. Thefirst balance weight 18, thesecond balance weight 19, and the swirlflow generating portion 21 are designed so that the relationship among these 1st to 3rd second moments of area satisfies the following equation (2). This makes it possible to make the swirl flow in theupper space 7 stronger and the swirl flow in thelower space 5 weaker. The "second moment of area of thefirst cross section 33" means a second moment of area calculated using Equation (1) for thefirst cross section 33. This also applies to thesecond cross section 34 and thethird cross section 35. -
- In the present embodiment, the swirl
flow generating portion 21 has a plurality ofbaffle plates 122. Therefore, the second term in the left-hand side of Equation (2) is represented as a sum of a plurality of 3rd second moments of area of the plurality ofbaffle plates 122. In the case where a plurality offirst balance weights 18 are provided, the first term in the left-hand side of Equation (2) is represented as a sum of a plurality of 1st second moments of area of the plurality offirst balance weights 18. Likewise, in the case where a plurality ofsecond balance weights 19 are provided, the right-hand side of Equation (2) is represented as a sum of a plurality of 2nd second moments of area of the plurality ofsecond balance weights 19. - In the present embodiment, the
second balance weight 19 is covered by acover 22 to reduce the area of thesecond displacement surface 19p of thesecond balance weight 19. Thesecond displacement surface 19p displaces the refrigerant. The area of thesecond displacement surface 19p is substantially zero, if the presence of screws or the like for fixing thecover 22 to therotor 15 is ignored. Therefore, the right-hand side of Equation (2) is zero and thus the relationship of Equation (2) is satisfied. - The 1st second moment of area MA1 is equal to the second moment of area of the first projected image on the first plane, when the first plane is determined so that the area of the first projected image has a maximum value. Likewise, the 2nd second moment of area MA2 is equal to the second moment of area of the second projected image on the second plane, when the second plane is determined so that the area of the second projected image has a maximum value. The 3rd second moment of area MA3 is equal to the second moment of area of the third projected image on the third plane, when the third plane is determined so that the area of the third projected image has a maximum value.
- Next, the flows of the refrigerant and the oil in the
closed casing 2 are described with reference toFig. 9 . InFig. 9 , the flow of the refrigerant in thelower space 5, the flow of the refrigerant in theupper space 7, and the flow of the oil returning from theupper space 7 to theoil reservoir 3 are indicated by anarrow 38a, anarrow 38b, and a dashedarrow 39, respectively. The oil held in theoil reservoir 3 is used for lubrication and sealing of the sliding parts of thecompression mechanism 4. The compressed refrigerant containing oil particles (oil mist) is discharged from thecompression mechanism 4 to thelower space 5 in a high-temperature and high-pressure state. In thelower space 5, a swirl flow field is formed by the rotation of therotor 15, but the intensity of the flow is reduced by the function of thecover 22, compared to that in theupper space 7. The refrigerant discharged into thelower space 5 is introduced from thelower space 5 to theupper space 7 through thecommunication passages 20. The refrigerant discharged into theupper space 7 is deflected in the swirling direction and the outer peripheral direction by centrifugal forces generated by thebaffle plates 122 serving also as the swirlflow generating portion 21 and thefirst balance weight 18 as well as a flow deflecting action performed by thebaffle plates 122 serving also as the swirlflow generating portion 21. Since the refrigerant travels in theupper space 7 while swirling, the oil particles are separated from the refrigerant by the centrifugal forces during travelling. Then, the refrigerant is discharged outside theclosed casing 2 through thedischarge pipe 8. The oil separated by the centrifugal forces in theupper space 7 adheres to the inner peripheral surface of thestator 14 or the inner wall of theclosed casing 2. Then, the oil returns to theoil reservoir 3 through theair gap 16 or theflow path 17. - Next, the actions of the swirl flow generating portion (baffle plate 122) and the swirl flow suppressing portion (cover 22) are described in detail.
- First, a flow field generated by a swirl flow is described. A model is assumed, in which a
rotor 37a is placed in acylindrical container 37 and therotor 37a is rotating about the central axis O1 of thecylindrical container 37, as shown inFig. 10 . In thecylindrical container 37, apressure field 37b is generated with a low pressure near the central axis O1 and a high pressure near the inner peripheral surface of thecylindrical container 37. This is the result of the effect of directing the flow radially outwardly by the centrifugal force of the flow itself and the effect of converting kinetic energy produced by swirling into pressure energy near the inner peripheral surface of thecylindrical container 37. - If the intensity of swirling increases, a
pressure field 37c indicated by a dashed line is generated. That is, the increase in the intensity of swirling increases the centrifugal force of the swirl flow itself. Therefore, thepressure field 37c tends to have an even lower pressure near the central axis O1 of thecylindrical container 37. On the other hand, kinetic energy produced by swirling with the inclusion of additional kinetic energy is converted into pressure energy near the inner peripheral surface of thecylindrical container 37. Therefore, thepressure field 37c tends to have an even higher pressure near the inner peripheral surface of thecylindrical container 37. - In order to increase the swirl flow without changing the rotational speed of the
rotor 37a, it is necessary to increase the displacement area of therotor 37a and thus increase the momentum added to the fluid. On the contrary, if the displacement area of therotor 37a is reduced, the swirl flow is suppressed. - In the present embodiment, from the viewpoint of preventing whirling, the
second balance weight 19 is heavier than thefirst balance weight 18. Typically, thebalance weights balance weights second balance weight 19 must be greater than that of thefirst balance weight 18 to make thesecond balance weight 19 heavier than thefirst balance weight 18. In the case where the volume of thesecond balance weight 19 is greater than that of thefirst balance weight 18 and thecover 22 is not provided, the area of thedisplacement surface 19p of thesecond balance weight 19 exceeds the area of thedisplacement surface 18 of thefirst balance weight 18. - Next, the flows of refrigerant and oil in a rotary compressor without a swirl flow generating portion and a swirl flow suppressing portion are described with reference to
Fig. 11 . Arotary compressor 100g shown inFig. 11 does not have components corresponding to the swirl flow generating portion (baffle plate 122) and the swirl flow suppressing portion (cover 22) in therotary compressor 100 of the present embodiment. Except for these components, the configuration of therotary compressor 100g is the same as that of therotary compressor 100 of the present embodiment. That is, afirst balance weight 18g and asecond balance weight 19g are each fixed to arotor 15g and rotate with therotor 15g. Thesecond balance weight 19g has a larger displacement area than thefirst balance weight 18g. Therefore, the swirl flow formed by thesecond balance weight 19g in alower space 5g is stronger than that formed by thefirst balance weight 18g in anupper space 7g. - In this case, as indicated by a dashed
line 140b inFig. 12 , a significant increase in pressure occurs in the opening of theflow path 17g on thelower space 5g side, on the basis of the theory described with reference toFig. 10 . As a result, as indicated by anarrow 138 inFig. 11 , the refrigerant is more likely to flow from thelower space 5g to theupper space 7g through theflow path 17g. - On the other hand, the oil separated by a centrifugal force in the
upper space 7g reaches the inner wall of theclosed casing 2g in theupper space 7g, and then returns to anoil reservoir 3g by its own weight through theflow path 17g. However, if the pressure in the opening of theflow path 17g on thelower space 5g side is excessively higher than that in the opening of theflow path 17g on theupper space 7g side, such a high pressure makes it difficult for the oil to return smoothly through theflow path 17g. That is, since the refrigerant travels from thelower space 5g to theupper space 7g mainly through theflow path 17g, the flow of the oil from theupper space 7g to thelower space 5g (indicated by a dashed arrow 139) is impeded. As a result, the oil is likely to accumulate near the inner wall of theclosed casing 2g in theupper space 7g. The accumulated oil is again mixed with the refrigerant and discharged with the refrigerant outside theclosed casing 2g. - In contrast, in the
rotary compressor 100 of the present embodiment, the swirl flow in theupper space 7 is increased by the function of the swirlflow generating portion 21 while the swirl flow in theloser space 5 is suppressed by the function of the swirlflow suppressing portion 22. Therefore, as indicated by asolid line 140a inFig. 12 , the pressure in the opening of theflow path 17 on theupper space 7 side is higher than that in the opening of theflow path 17 on thelower space 5 side, or the difference between the pressure in the opening of theflow path 17 on theupper space 7 side and that in the opening of theflow path 17 on thelower space 5 side is relatively small. - Furthermore, as described with reference to
Fig. 10 , the pressure near the center of therotor 15 decreases when the swirl flow is increased, while it increases when the swirl flow is suppressed. When the swirlflow generating portion 21 is provided in theupper space 7 and the swirlflow suppressing portion 22 is provided in thelower space 5, the pressure near the center of therotor 15 becomes lower in theupper space 7 and higher in thelower space 5. As a result, the amount of refrigerant flowing from thelower space 5 to theupper space 7 through thecommunication passage 20 increases, and the refrigerant can be prevented from flowing from theupper space 7 to thelower space 5 through theflow path 17, or the amount of refrigerant flowing from thelower space 5 to theupper space 7 through theflow path 17 decreases significantly. When the amount of refrigerant flowing from thecompression mechanism 4 to thedischarge pipe 8 through theflow path 17 decreases, the oil can be returned from theupper space 7 to theoil reservoir 3 smoothly through theflow path 17. - Next, consideration is given to a second moment of area.
- Generally, the intensity of a swirl flow applied to a flow field is determined by a swirl momentum Kr represented by the following equation (3). In Equation (3), p is the density of a fluid, V is the rotational speed of a rotor, ω is the angular velocity of the rotor, r is the turning radius of a displacement portion (displacement surface) of the rotor, and A is the projected area of the displacement portion (displacement surface) of the rotor.
-
- In Equation (3), assuming that the rotational speed V of the rotor is far below 0.3 times the sound velocity in a refrigerant flow, the refrigerant can be regarded as an incompressible fluid. In this case, the density p is constant. Furthermore, the angular velocity ω also is constant under the same operating conditions. As a result, the swirl momentum Kr that contributes to the intensity of the swirl flow applied to the flow field is proportional to a value obtained by multiplying the square of the turning radius r by the projected area A. The value obtained by multiplying the square of the turning radius r by the projected area A corresponds to the second moment of area described above. That is, the second moment of area represents the intensity of swirling applied to the refrigerant flow. The smaller the second moment of area, the smaller the intensity of swirling given to the refrigerant flow. Therefore, when a strong swirl flow must be generated in the
upper space 7, the second moments of area of thefirst balance weight 18 and the swirlflow generating portion 21 must be increased. When a swirl flow in thelower space 5 must be suppressed, the second moment of area of thesecond balance weight 19 must be decreased using the swirlflow suppressing portion 22. - Next, the effect obtained by covering the outlet of the
communication passage 20 with the baffle plate 122 (discharge direction deflecting portion) of the swirlflow generating portion 21 is described. - First, an example where nothing but a
balance weight 18g is provided on the top of arotor 15g (in thecompressor 100g shown inFig. 11 ), as shown inFig. 13A and Fig. 13B , is described. InFig. 13B , the rotational direction of therotor 15g is considered as a static system. Probably, arefrigerant flow 42g discharged from acommunication passage 20g to anupper space 7g collides with arefrigerant flow 41g in theupper space 7g at an almost right angle. In this case, a large pressure loss may occur. When a large pressure loss occurs at the outlet of thecommunication passage 20g, the flow rate of the refrigerant flowing upward through thecommunication passage 20g decreases relatively, while the flow rate of the refrigerant flowing through theair gap 16g or theflow path 17g increases relatively. As described above, when the refrigerant flow rate in theflow path 17g increases, the amount of oil discharged from thecompressor 100g also increases. - Next, an example where
baffle plates 21g are disposed at the outlets of thecommunication passages 20g, as shown inFig. 14A and Fig. 14B , is described. Each of thebaffle plates 21g is located in the rotational direction of therotor 15g with respect to the outlet of thecommunication passage 20g. Thebaffle plate 21g extends straight in a direction parallel to the rotational axis O, and thus does not cover the outlet of thecommunication passage 20g. Such abaffle plate 21g can prevent therefrigerant flow 42g from colliding with therefrigerant flow 41g at a right angle. This means that the pressure loss at the outlet of thecommunication passage 20 can be reduced. It should be noted that thebaffle plate 21g has no ability to deflect the refrigerant flow. Therefore, as shown inFig. 17 , the refrigerant tends to flow upward in the vertical direction. - Next, the present embodiment in which baffle
plates 122 are disposed to cover the outlets of thecommunication passages 20, as shown inFig. 15A and Fig. 15B , is described. Since arefrigerant flow 42 discharged from thecommunication passage 20 to theupper space 7 is subjected to the deflecting action of thebaffle plate 122, the refrigerant is discharged in the opposite rotational direction of therotor 15. That is, the refrigerant travels from thecommunication passages 20 to theupper space 7, while being deflected in a direction inclined with respect to the direction parallel to the rotational axis O. Then, as shown inFig. 16 , a swirl flow begins to be formed at a position relatively close to the upper surface of therotor 15. As a result, the flow distance (time) of the refrigerant in theupper space 7 increases, which can promote the centrifugal separation of oil. - The
baffle plate 122 may completely cover the outlet of thecommunication passage 20 in plan view, or may partially cover it. That is, a projected image obtained by projecting thebaffle plate 122 onto the upper surface of therotor 15 may contain the opening area of thecommunication passage 20, or the projected image of thebaffle plate 122 may overlap the opening area. For example, experimental results under high load conditions (a high rotational speed and a high pressure ratio) show that an excellent effect is obtained when thebaffle plate 122 covers about 85% of the opening area. -
Fig. 18 is a graph showing the results of experiments conducted to ascertain the effect of therotary compressor 100 of the present embodiment. The vertical axis represents the amount of discharged oil. The experiments were conducted under high load conditions, and the amount of oil discharged with the refrigerant through the discharge pipe was measured. The amount of the discharged oil was evaluated by sampling the refrigerant at the outlet of a condenser in a refrigeration cycle. "Embodiment" shows the measurement result in the rotary compressor described with reference toFig. 1 , etc. "Comparative Example" shows the measurement result in a rotary compressor in which the swirlflow generating portion 21 and the swirl flow suppressing portion 22 (cover) of the rotary compressor of the embodiment are removed. "First Modification" shows the measurement result in a rotary compressor according to a first modification described later. The amount of oil discharged from the rotary compressor of the present embodiment was small, i.e., "0.44", when the amount of oil discharged from the rotary compressor of Comparative Example was "1". The amount of oil discharged from the rotary compressor of the first modification described later was even smaller, i.e., "0.1". - As shown in
Fig. 19 , in arotary compressor 101 according to the first modification, the inlet of thedischarge pipe 8 is located near the upper surface of therotor 15. More specifically, the lower end of thedischarge pipe 8 is located below the upper end of thestator 14 in the direction parallel to the rotational axis O of the shaft 9 (i.e., the vertical direction). The rotational axis O of theshaft 9 passes through the inlet of thedischarge pipe 8. More specifically, the rotational axis O of theshaft 9 coincides with the center of the inlet of thedischarge pipe 8. - A refrigerant is discharged from the
communication passage 20 to theupper space 7, and then travels, while swirling and being deflected, toward the inner wall of theclosed casing 2 by the centrifugal force and the action of thebaffle plates 122. Then, the refrigerant goes downward along the outer peripheral surface of thedischarge pipe 8 while swirling and enters thedischarge pipe 8. Since the flow distance (time) of the refrigerant flow in theupper space 7 can be increased, the separation of oil can further be promoted. Furthermore, since the refrigerant forms a downflow immediately before it enters thedischarge pipe 8, the oil separation by the weight of the refrigerant itself also can be promoted. As a result, as shown inFig. 18 , the amount of discharged oil can further be reduced. - In a modification shown in
Fig. 20 , aspace filling member 22b is used instead of thecover 22 as a swirl flow suppressing portion. Thespace filling member 22b has a smaller specific gravity than thesecond balance weight 19, and is provided along the rotational trajectory of thesecond balance weight 19. That is, thespace filling member 22b is disposed symmetrically to thesecond balance weight 19 with respect to a plane including the rotational axis O, and fills the space along the trajectory of thesecond balance weight 19. The area of the displacement surface of thesecond balance weight 19 can be reduced by thespace filling member 22b, like thecover 22 described with reference toFig. 1 , etc. - Preferably, the
space filling member 22b is made of a material having voids into which the refrigerant containing oil particles can penetrate. Typically, thespace filling member 22b can be made of a material having voids, such as foamed materials, metal fiber woven materials, and steel wool. Since these materials are relatively light in weight, the function of thesecond balance weight 19 as a balance weight is less likely to be impaired. - The shape of the
space filling member 22b is not particularly limited as long as the area of the displacement surface of thesecond balance weight 19 can be reduced. In the modification shown inFig. 20 , the shape of thespace filling member 22b is determined so that the area of the displacement surface of thesecond balance weight 19 is substantially zero. The area of the displacement surface of thespace filling member 22b also is zero. That is, a combination of thesecond balance weight 19 and thespace filling member 22b forms an annular shape. - The refrigerant flow around the
second balance weight 19 contains oil particles. Thespace filling member 22b is fixed to therotor 15, and rotates with therotor 15. Therefore, a shear flow is formed between thespace filling member 22b and the refrigerant flow. In the case where thespace filling member 22b is made of a material having voids such as a foamed material, oil particles enter the foamed material due to turbulence in the refrigerant flow, etc. Thereby, thespace filling member 22b serves as an oil mist trap. - As shown in
Fig. 21 , adischarge port 25 for discharging the refrigerant compressed in thecompression mechanism 4 to thelower space 5 may be formed at a position where it overlaps thesecond balance weight 19 and thespace filling member 22b, that is, a position where thedischarge port 25 overlaps the rotational trajectory of thesecond balance weight 19, in the direction parallel to the rotational axis O (i.e., in the vertical direction). In still other words, when thedischarge port 25, thesecond balance weight 19, and thespace filling member 22b are projected on a plane perpendicular to the rotational axis O, the projected image of thedischarge port 25 may overlap the projected image of thesecond balance weight 19 and/or the projected image of thespace filling member 22b. In this configuration, the refrigerant discharged to thelower space 5 through thedischarge port 25 can collide directly with thespace filling member 22b. As a result, the amount of oil particles entering the voids in thespace filling member 22b increase, and the oil separation effect of thespace filling member 22b can be sufficiently obtained. - As shown in
Fig. 22 , acover 22c as a swirl flow suppressing portion may be formed integrally with the end plate for clamping and fixing the stack ofsteel plates 28 constituting therotor 15. Thereby, the number of components can be reduced. Thecover 22c has an annular shape in plan view. In thecover 22c, a plurality of through-holes 44 are each formed at a position corresponding to the inlet of thecommunication passage 20. The refrigerant can move from thelower space 5 to thecommunication passages 20 through the through-holes 44 and the interior of thecover 22c. - A swirl
flow generating portion 146 shown inFig. 23 has anend plate 27 and afirst balance weight 18 integrated with theend plate 27. That is, theend plate 27 and thefirst balance weight 18 are formed as a single component by a casting method or the like. This can reduce the number of components and simplify the assembly process of the compressor. - The
end plate 27 is caulked and fixed to the stack ofsteel plates 28 to form therotor 15. Thecommunication passages 20 of therotor 15 are covered byroof portions 46 provided on theend plate 27. Theroof portion 46 constitutes a discharge direction deflecting portion. Oneroof portion 46 is provided for onecommunication passage 20. Theroof portion 46 has walls above the outlet of thecommunication passage 20, downstream thereof in the rotational direction of therotor 15, on the radially inner peripheral side, and on the radially outer peripheral side. In other words, theroof portion 46 has the shape of a small box with an opening only in the opposite rotational direction of therotor 15. The refrigerant is discharged from thecommunication passage 20 in the opposite rotational direction of therotor 15 by the function of theroof portions 46. - As shown in
Fig. 24A , in the present modification, anoutlet part 48 of thecommunication passage 20 extends in a direction inclined with respect to the direction parallel to the rotational axis O of themotor 6. By the function of theoutlet part 48, the compressed refrigerant travels from thecommunication passage 20 to theupper space 7, while being deflected in a direction that is opposite to the rotational direction of therotor 15 and is inclined with respect to the direction parallel to the rotational axis O. That is, the discharge direction deflecting portion is constituted by theoutlet part 48. Also in this modification, arefrigerant flow 42 from thecommunication passage 20 does not collide with arefrigerant flow 41 at a right angle in theupper space 7. Therefore, an increase in the pressure loss at the outlet of thecommunication passage 20 can be prevented. -
Fig. 24A does not indicate a swirl flow generating portion for increasing a swirl flow. However, the swirl flow generating portion (for example, thebaffle plate 122 shown inFig. 3 ) may be provided at a position where it does not cover the outlet of thecommunication passage 20. - In a modification shown in
Fig. 24B , abaffle plate 122 protruding obliquely from the upper surface of therotor 15 so as to extend in the same direction as theoutlet part 48 is provided as a swirl flow generating portion. An image obtained by projecting thebaffle plate 122 onto the upper surface of therotor 15 overlaps the outlet of thecommunication passage 20. This means that in this modification, both theoutlet part 48 and thebaffle plate 122 have the function as a discharge direction deflecting portion. This configuration ensures that a refrigerant flow from thecommunication passage 20 is directed toward the opposite rotational direction of therotor 15. This configuration has the potential to further reduce the pressure loss that occurs when therefrigerant flow 42 is deflected. - The configurations of the first to sixth modifications can be arbitrarily combined in the
rotary compressor 100 shown inFig. 1 , without departing from the spirit and scope of the present invention. Furthermore, the present invention is not limited to a rotary compressor, and can be applied to other hermetic compressors. - The hermetic compressor of the present invention is suitably applicable to refrigeration cycle apparatuses used for air conditioners, water heaters, etc. Since the flow of oil into a condenser and an evaporator of a refrigeration cycle apparatus can be reduced, the heat exchange efficiency of the condenser and the evaporator can be improved.
Claims (11)
- A hermetic compressor comprising:a closed casing having an oil reservoir in its bottom portion;a compression mechanism, disposed in the closed casing, for compressing a working fluid;a motor, disposed above the compression mechanism in the closed casing, for driving the compression mechanism, the motor having a rotor and a stator;an upper space, formed above the motor, as a part of an internal space of the closed casing;a lower space, formed between the motor and the compression mechanism, as a part of the internal space of the closed casing;a discharge pipe opening into the upper space, for discharging the compressed working fluid outside the hermetic compressor;a first balance weight protruding from an upper surface of the rotor toward the upper space;a swirl flow generating portion protruding from the upper surface of the rotor toward the upper space, the swirl flow generating portion being disposed at a position closer to a rotational axis of the motor than the first balance weight;a second balance weight protruding from a lower surface of the rotor toward the lower space; anda communication passage formed in the rotor so as to introduce, into the upper space, the working fluid compressed in the compression mechanism and discharged to the lower space, whereinwhen a three-dimensional annular trajectory of the first balance weight formed around the rotational axis when the motor is driven is defined as a first trajectory, a plane obtained by cutting the first trajectory with a first plane parallel to the rotational axis and including the rotational axis is defined as a first cross section, a three-dimensional annular trajectory of the second balance weight formed around the rotational axis when the motor is driven is defined as a second trajectory, a plane obtained by cutting the second trajectory with a second plane parallel to the rotational axis and including the rotational axis is defined as a second cross section, a three-dimensional annular trajectory of the swirl flow generating portion formed around the rotational axis when the motor is driven is defined as a third trajectory a plane obtained by cutting the third trajectory with a third plane parallel to the rotational axis and including the rotational axis is defined as a third cross section, an area of a micro-region included in a specific region on an arbitrary plane parallel to the rotational axis and including the rotational axis is defined as dA, a distance from the rotational axis to a centroid of the micro-region is defined as r, and a value MA represented by the following equation (1) is defined as a second moment of area, [Equation 1]
a sum of a second moment of area of the first cross section and a second moment of area of the third cross section is greater than a second moment of area of the second cross section, andthe hermetic compressor further comprises a discharge direction deflecting portion for causing the compressed working fluid to travel from the communication passage to the upper space, while deflecting the working fluid in a direction inclined with respect to a direction parallel to the rotational axis. - The hermetic compressor according to claim 1, wherein the swirl flow generating portion is also used as the discharge direction deflecting portion.
- The hermetic compressor according to claim 1 or 2, wherein the discharge direction deflecting portion is configured to direct the compressed working fluid in a direction opposite to a rotational direction of the rotor.
- The hermetic compressor according to claim 2, wherein
the swirl flow generating portion includes, as the discharge direction deflecting portion, a baffle plate protruding from the upper surface of the rotor toward the upper space, and
an image obtained by projecting the baffle plate onto the upper surface of the rotor overlaps an outlet of the communication passage. - The hermetic compressor according to claim 1, wherein
an outlet part of the communication passage extends in the direction inclined with respect to the direction parallel to the rotational axis so that the compressed working fluid travels from the communication passage to the upper space, while being deflected in a direction that is opposite to a rotational direction of the rotor and is inclined with respect to the direction parallel to the rotational axis, and
the discharge direction deflecting portion is constituted by the outlet part. - The hermetic compressor according to claim 5, wherein
the swirl flow generating portion includes a baffle plate protruding obliquely from the upper surface of the rotor so as to extend in the same direction as the outlet part, and
an image obtained by projecting the baffle plate onto the upper surface of the rotor overlaps an outlet of the communication passage. - The hermetic compressor according to any one of claims 1 to 6, further comprising a swirl flow suppressing portion for reducing an area of a displacement surface of the second balance weight, the displacement surface displacing the working fluid.
- The hermetic compressor according to claim 7, wherein the swirl flow suppressing portion is constituted by a cover that covers the second balance weight so that the area of the displacement surface of the second balance weight is zero, the displacement surface displacing the working fluid.
- The hermetic compressor according to claim 8, wherein the cover is formed integrally with an end plate for clamping and fixing constituent elements of the rotor.
- The hermetic compressor according to claim 7, wherein
the swirl flow suppressing portion is provided along a rotational trajectory of the second balance weight, and
the swirl flow suppressing portion has a smaller specific gravity than the second balance weight. - The hermetic compressor according to claim 10, wherein the swirl flow suppressing portion is made of a material having voids into which the working fluid containing oil particles can penetrate.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010185878 | 2010-08-23 | ||
PCT/JP2011/004543 WO2012026081A1 (en) | 2010-08-23 | 2011-08-10 | Hermetically sealed compressor |
Publications (1)
Publication Number | Publication Date |
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EP2610491A1 true EP2610491A1 (en) | 2013-07-03 |
Family
ID=45723103
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP11819557.7A Withdrawn EP2610491A1 (en) | 2010-08-23 | 2011-08-10 | Hermetically sealed compressor |
Country Status (5)
Country | Link |
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US (1) | US20120269667A1 (en) |
EP (1) | EP2610491A1 (en) |
JP (1) | JP5632465B2 (en) |
CN (1) | CN102510951A (en) |
WO (1) | WO2012026081A1 (en) |
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KR101188558B1 (en) * | 2008-08-05 | 2012-10-08 | 미쓰비시덴키 가부시키가이샤 | Induction motor and elclosed compressor |
JP6692465B2 (en) * | 2017-02-02 | 2020-05-13 | 三菱電機株式会社 | Rotating electric machine |
JP6720995B2 (en) * | 2018-03-15 | 2020-07-08 | 株式会社富士通ゼネラル | Compressor |
CN112005016B (en) * | 2018-04-24 | 2022-05-13 | 大金工业株式会社 | Compressor |
KR102051097B1 (en) * | 2018-06-07 | 2019-12-02 | 엘지전자 주식회사 | Compressor |
JP6648785B2 (en) | 2018-07-11 | 2020-02-14 | 株式会社富士通ゼネラル | Compressor |
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CN113719914B (en) * | 2021-09-06 | 2024-03-29 | 广东美的暖通设备有限公司 | Module mechanism, air conditioner outdoor unit and air conditioning system |
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Also Published As
Publication number | Publication date |
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US20120269667A1 (en) | 2012-10-25 |
CN102510951A (en) | 2012-06-20 |
JPWO2012026081A1 (en) | 2013-10-28 |
WO2012026081A1 (en) | 2012-03-01 |
JP5632465B2 (en) | 2014-11-26 |
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