WO2020008902A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
WO2020008902A1
WO2020008902A1 PCT/JP2019/024576 JP2019024576W WO2020008902A1 WO 2020008902 A1 WO2020008902 A1 WO 2020008902A1 JP 2019024576 W JP2019024576 W JP 2019024576W WO 2020008902 A1 WO2020008902 A1 WO 2020008902A1
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WO
WIPO (PCT)
Prior art keywords
scroll
compression
chamber
path
compression chamber
Prior art date
Application number
PCT/JP2019/024576
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English (en)
Japanese (ja)
Inventor
裕文 吉田
啓晶 中井
護 西部
淳 作田
Original Assignee
パナソニックＩｐマネジメント株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by パナソニックＩｐマネジメント株式会社 filed Critical パナソニックＩｐマネジメント株式会社
Publication of WO2020008902A1 publication Critical patent/WO2020008902A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents

Definitions

  • the present disclosure relates to a scroll compressor used for an air conditioner, a refrigerator, a blower, a water heater, and the like.
  • a scroll compressor used in a refrigeration cycle of a conventional air conditioner or the like has, for example, a configuration shown in FIG.
  • the sealed container 101 serving as the outer casing of the compressor has both ends closed.
  • An electric motor 102 and a compression mechanism 103 are built in the sealed container 101.
  • the compression mechanism 103 mainly includes the crankshaft 104, the main bearing 105, and the compression element 106.
  • the electric motor 102 includes a stator 102a fixed to the inner wall surface side of the closed casing 101, and a rotor 102b rotatably supported inside the stator 102a.
  • the crankshaft 104 is connected to the rotor 102b in a penetrating state.
  • the oil stored in the lower part of the closed casing 101 is supplied to each sliding part of the compression mechanism 103.
  • the oil rides on the flow of the gas compressed in the compression element 106 and is separated into gas and liquid before flowing out of the compressor from a discharge pipe 107 provided at the upper portion of the closed vessel 101.
  • the oil is then recirculated to the lower oil sump.
  • a plurality of compression chambers 110 are formed by engaging the fixed scroll 108 and the orbiting scroll 109 on which the spiral wraps 108a and 109a are respectively formed.
  • the orbiting scroll 109 is connected to the crankshaft 104 having the eccentric part, and the orbiting scroll 109 is caused to orbit using the Oldham ring 112 while preventing rotation.
  • the gas is compressed while reducing the volume of the compression chamber 110 toward the center.
  • the compressed gas is discharged to the outside of the compression mechanism 103 through a main discharge port 113 provided at the center of the fixed scroll 108 and a bypass discharge port 114 opened to the compression chamber 110 during compression. .
  • the back pressure adjusting valve 115 has a function of holding the orbiting scroll 109 against the fixed scroll 108 while maintaining an intermediate pressure higher than the suction pressure.
  • the back pressure adjusting valve 115 prevents compression leakage caused by separation between the orbiting scroll 109 and the fixed scroll 108, that is, a so-called overturn phenomenon.
  • Such a scroll compressor is configured to appropriately maintain the pressure in the back pressure chamber (for example, see Patent Literature 1 and Patent Literature 2).
  • FIG. 10 shows a scroll compressor of Patent Document 1.
  • a high-pressure area 202 and a back pressure chamber 203 are formed on the back surface of the orbiting scroll 201.
  • a first path 204 that intermittently communicates the high-pressure region 202 with the back pressure chamber 203 and a second path 206 that intermittently communicates the back pressure chamber 203 with the compression chamber 205 are provided.
  • An appropriate amount of oil can be supplied to both the first compression chamber 205a on the wrap outer wall side and the second compression chamber 205b on the wrap inner wall side of the orbiting scroll 201, so that high efficiency and high reliability will be realized.
  • the scroll compressor disclosed in Patent Document 2 has a configuration in which the second path 206 and the bypass discharge port 207 are intermittently communicated. This suppresses over-compression, particularly during low-speed, low-compression-ratio operation, suppresses an excessive rise in the pressure of the back pressure chamber 203, and reduces sliding loss in the thrust bearing.
  • the present disclosure has been made in view of such a point, and provides a scroll compressor that exhibits high efficiency by preventing the back pressure chamber from being in an excessive gas state.
  • a scroll compressor includes a head plate, a fixed scroll having a spiral wrap rising from the head plate, an orbiting scroll, a compression chamber formed between the fixed scroll and the orbiting scroll by meshing the fixed scroll and the orbiting scroll. And a high-pressure area and a back-pressure chamber formed on the back surface of the orbiting scroll.
  • the orbiting scroll orbits with a predetermined orbital radius along a circular orbit under the control of the rotation restricting mechanism. Due to the turning of the orbiting scroll, the compression chamber moves toward the center while changing the volume.
  • the scroll compressor performs a series of operations of suction, compression, and discharge.
  • the scroll compressor has a main discharge port provided at a central portion of the fixed scroll, a bypass discharge port provided to communicate with the compression scroll and the compression chamber in the middle of the fixed scroll, and a first communication port connecting the high pressure region and the back pressure chamber. And a second path intermittently connecting the back pressure chamber and the compression chamber. The communication of the second path is finished before the communication between the bypass discharge port and the compression chamber is established by the turning of the orbiting scroll.
  • bypass discharge port and the second path are designed to have a timing that simultaneously communicates with the compression chamber, the discharged gas that has flowed back through the bypass discharge port reaches the back pressure chamber through the second path. Then, the back pressure chamber becomes in an excessive gas state, which causes a decrease in the amount of oil supplied to the compression chamber.
  • the discharged gas that has flowed back through the bypass discharge port does not reach the back pressure chamber. Therefore, it is possible to prevent the back pressure chamber from being in an excessive gas state.
  • FIG. 1 is a cross-sectional view of the scroll compressor according to the first embodiment of the present disclosure as viewed from a side.
  • FIG. 2 is an enlarged cross-sectional view of a main part of the scroll compressor as viewed from the side.
  • FIG. 3 is a diagram showing a cross-sectional configuration of a main part in the cross section aa of FIG.
  • FIG. 4 is a diagram showing a cross-sectional configuration of main components in the cross section aa of FIG.
  • FIG. 5 is a diagram showing a cross-sectional configuration of main components in a bb cross-section of FIG.
  • FIG. 6 is a diagram showing a cross-sectional configuration of main components in a bb cross-section of FIG.
  • FIG. 1 is a cross-sectional view of the scroll compressor according to the first embodiment of the present disclosure as viewed from a side.
  • FIG. 2 is an enlarged cross-sectional view of a main part of the scroll compressor as viewed from the side.
  • FIG. 7 is a diagram showing a cross-sectional configuration of main components in a bb cross-section of FIG.
  • FIG. 8 is a diagram showing a cross-sectional configuration of a main part in a bb cross section of FIG.
  • FIG. 9 is a diagram showing a cross-sectional configuration of a conventional scroll compressor as viewed from the side.
  • FIG. 10 is a cross-sectional view of a compression mechanism in a scroll compressor described in Patent Document 1.
  • a scroll compressor includes a fixed scroll having a head plate and a spiral wrap rising from the head plate, an orbiting scroll, and a fixed scroll and an orbiting scroll that are formed between the fixed scroll and the orbiting scroll. And a high-pressure area and a back-pressure chamber formed on the back of the orbiting scroll.
  • the orbiting scroll orbits with a predetermined orbital radius along a circular orbit under the control of the rotation restricting mechanism. Due to the turning of the orbiting scroll, the compression chamber moves toward the center while changing the volume.
  • the scroll compressor performs a series of operations of suction, compression, and discharge.
  • the scroll compressor communicates the main discharge port provided at the center of the fixed scroll, the fixed scroll with the compression chamber, a bypass discharge port provided so as to communicate with the middle of compression, and the high pressure region and the back pressure chamber.
  • a first path and a second path intermittently connecting the back pressure chamber and the compression chamber are provided. The communication of the second path is finished before the communication between the bypass discharge port and the compression chamber is established by the turning of the orbiting scroll.
  • the first path intermittently communicates the high-pressure region with the back pressure chamber, the communication timing between the first path and the back pressure chamber, and the communication between the second path and the back pressure chamber.
  • the configuration may be different from the timing.
  • the first path and the second path do not communicate simultaneously with the back pressure chamber. Therefore, the oil flowing into the back pressure chamber from the first path does not cause a pressure increase in the compression chamber due to flowing into the compression chamber through the second path while the pressure is insufficiently reduced. It is possible to prevent a rise in power and maintain high efficiency.
  • the oil flowing into the compression chamber and supplied to the lubrication may be compatible with the working fluid at a temperature of 50 ° C. or higher.
  • the bypass discharge port and the second path do not communicate with the compression chamber at the same time.
  • an excessive gas state due to foaming of the oil in the back pressure chamber can be prevented, and the oil supply to the compression chamber can be ensured. Therefore, it is possible to realize low friction sliding of the thrust bearing and the scroll lap sliding portion in a good lubricating state, and to reduce the compression loss by reliably sealing the compression chamber.
  • FIG. 1 is a cross-sectional view of a scroll compressor 50 according to a first embodiment of the present disclosure as viewed from the side, and FIG. It is sectional drawing seen.
  • the scroll compressor 50 includes a closed container 1 and a discharge pipe 2.
  • the entire interior of the sealed container 1 is in a discharge pressure atmosphere communicating with the discharge pipe 2.
  • the electric motor 3 is arranged at the center of the sealed container 1 and the compression mechanism is arranged at the upper part.
  • a main body frame 5 of a compression mechanism that supports one end of a crankshaft 4 fixed to a rotor 3 a of the electric motor 3 is fixed to the closed casing 1.
  • a fixed scroll 6 is attached to the main body frame 5.
  • the main shaft direction oil passage 7 provided in the crankshaft 4 has one end communicating with the oil supply pump device 8 and the other end finally communicating with the eccentric bearing 10 of the orbiting scroll 9.
  • the orbiting scroll 9 meshes with the fixed scroll 6 to form the compression chamber 11.
  • the orbiting scroll 9 has a spiral orbiting scroll wrap 9a and a orbiting end plate 9b on which the orbiting scroll wrap 9a and the eccentric bearing 10 stand upright.
  • the orbiting scroll 9 is arranged between the fixed scroll 6 and the main body frame 5.
  • the fixed scroll 6 includes a fixed end plate 6a and a spiral fixed scroll wrap 6b.
  • a main discharge port 12 and a bypass discharge port 13 including a plurality of holes for discharging gas in the compression chamber 11 when the inside reaches a required discharge pressure during compression are arranged.
  • a suction port 14 and a suction chamber 15 which is a fluid passage until compression is started are arranged on an outer peripheral portion of the fixed scroll wrap 6b.
  • An eccentric shaft 17 eccentric from the main shaft 16 of the crankshaft 4 and arranged at the upper end of the crankshaft 4 is configured to engage and slide with the eccentric bearing 10 of the orbiting scroll 9.
  • the main shaft 16 engages and slides with the main bearing 18 of the main body frame 5.
  • An annular seal member 19 concentric with the main bearing 18 is mounted on the main body frame 5 in a loose state.
  • the annular seal member 19 divides a rear chamber 20 inside, which is generally at a discharge pressure atmosphere, and a back pressure chamber 21 outside, which is at an intermediate pressure atmosphere.
  • the oil sucked up by the oil supply pump device 8 is oil that is compatible with the working fluid at a temperature of 50 ° C. or higher.
  • the oil passes through the oil passage 7 of the crankshaft 4 and is guided to an internal space 22 formed between the orbiting scroll 9 and the eccentric shaft 17.
  • One of the oils passes through a first path 23 provided on the back surface of the orbiting scroll 9b of the orbiting scroll 9 to a back pressure chamber 21 formed by being surrounded by the fixed scroll 6 and the main body frame 5. .
  • the oil is guided to the compression chamber 11 through the second path 24 provided in the orbiting scroll 9 and the counterbore 25 provided on the bottom surface 6c of the fixed scroll wrap 6b.
  • the back pressure chamber 21 is maintained at the pressure of the compression chamber 11 during compression, which communicates with the second path 24, and presses the orbiting scroll 9 against the fixed scroll 6.
  • the orbiting end plate 9b, the upper surface 6d of the fixed scroll wrap 6b and the fixed end plate 6a form the thrust bearing 26.
  • the other part of the oil is discharged to the outside of the compression mechanism through the eccentric bearing 10, the back chamber 20, and the main bearing 18.
  • the check valve device 27 that opens and closes the outlet side of the main discharge port 12 is mounted on a plane of the fixed scroll 6 opposite to the lap side of the fixed end plate 6a.
  • the check valve device 27 includes a reed valve 27a made of a thin steel plate and a valve retainer 27b.
  • the lower end of the crankshaft 4 is supported by the auxiliary bearing 28 fixed by welding or shrink fitting in the closed container 1, and the crankshaft 4 rotates stably.
  • the auxiliary bearing 28 has a journal bearing configuration, and part of the oil sucked up by the oil supply pump device 8 is supplied to the auxiliary bearing 28.
  • the gas immediately after being compressed by the compression mechanism and discharged from the main discharge port 12 and the gas immediately before being discharged from the discharge pipe 2 to the outside of the closed container 1 are separated by the muffler 29.
  • the gas in the discharge chamber 30 inside the muffler 29 passes through a downward gas flow path 31 provided near the outer periphery of the compression mechanism, and is guided to the upper part of the rotor 3a as shown by a dotted arrow in the figure.
  • the gas merges with the oil discharged after lubricating the main bearing 18 and the like, and reaches the lower part of the rotor 3a through a rotor passage 3b provided inside the rotor 3a.
  • the mixed flow of gas and oil collides with the lower coil end of the stator 3c by centrifugal force, and is separated into gas and liquid.
  • the gas after the gas-liquid separation is guided to the space above the stator 3c through the stator passage 3d provided on the outer periphery of the stator 3c.
  • This space is a space separated from the space above the rotor 3a by the partition member 32.
  • the gas passes through an upward gas flow path (not shown) provided in the compression mechanism, reaches a space above the compression mechanism, and is discharged from the discharge pipe 2 to the outside of the closed container 1.
  • FIGS. 3 and 4 are views showing the configuration of main parts in the cross section aa in FIG.
  • the trajectory in which the first path 23 provided in the orbiting scroll 9 makes the orbital movement along with the rotation of the crankshaft 4 is indicated by a chain line.
  • FIGS. 5 to 8 are views showing the configuration of the main parts in the bb cross section in FIG. 1, and show how the orbiting scroll 9 performs the orbiting motion.
  • the trajectory along which the second path 24 provided in the orbiting scroll 9 orbits along with the rotation of the crankshaft 4 is indicated by a chain line.
  • the main discharge port 12, the bypass discharge port 13, and the bottom counterbore 25 provided on the bottom surface 6c of the fixed scroll wrap are indicated by two-dot chain lines.
  • Each of the compression chambers (the first compression chamber 11a and the second compression chamber 11b) performs a compression operation independently, and the compressed gas / liquid is discharged from the main discharge port 12 after merging at the center.
  • the compressed gas / liquid is supplied to the first bypass discharge port 13a provided in the middle of the compression of the first compression chamber 11a, and provided in the middle of the compression of the second compression chamber 11b.
  • the second bypass discharge port 13b is also discharged.
  • the first path 23 pivots over the annular seal member 19 shown by the dotted line. At the crank angle shown in FIG. 3, the first path 23 opens into the back chamber 20 at the discharge pressure.
  • the internal space 22 on the upstream side of the first path 23 and the rear chamber 20 on the downstream side of the first path 23 are both in a discharge pressure atmosphere. Therefore, there is no oil flow in the first path 23.
  • the first path 23 opens to the back pressure chamber 21 at the intermediate pressure. Due to the pressure difference between the internal space 22 at the discharge pressure and the back pressure chamber 21 at the intermediate pressure, oil flows into the back pressure chamber 21 from the first path 23.
  • the amount of oil supplied to the back pressure chamber 21 is controlled to an appropriate amount.
  • the first bottom counterbore 25a of the two bottom counterbores 25 and the second path 24 overlap.
  • the back pressure chamber 21 communicates with the first compression chamber 11a, and the oil in the back pressure chamber 21 flows into the first compression chamber 11a and is provided for lubrication and sealing.
  • the respective compression chambers (the first compression chamber 11a and the second compression chamber 11b) are not simultaneously opened to the second path 24 and the respective bypass discharge ports 13a and 13b. Therefore, the discharged gas that has flowed back through the bypass discharge port 13 from the discharge chamber 30 in the atmosphere with the highest pressure immediately after compression does not reach the back pressure chamber 21 through the second path 24. . Thereby, it is possible to prevent the shortage of the refueling amount due to the excessive gas state of the back pressure chamber 21 that occurs when the gas reaches the back pressure chamber 21.
  • the lubrication of the thrust bearing 26 and the sliding portions of the fixed scroll wrap 6b and the orbiting scroll wrap 9a can be realized by a good lubrication state, and the compression chamber can be reliably supplied with lubrication to the compression chamber 11. 11 can reduce the compression loss by the reliable seal.
  • the first path 23 intermittently connects the internal space 22 and the back pressure chamber 21.
  • the communication timing between the first path 23 and the back pressure chamber 21 and the communication timing between the second path 24 and the back pressure chamber 21 are shifted so that the first path 23 and the second path 24 Are not configured to communicate at the same time.
  • the oil that has flowed into the back pressure chamber 21 from the first path 23 flows into the compression chamber 11 through the second path 24 with insufficient pressure reduction, causing an increase in the pressure of the compression chamber 11. None. Therefore, it is possible to prevent a rise in compression power and maintain high efficiency.
  • the oil used for lubrication is compatible with the working fluid at a temperature of 50 ° C or higher. Therefore, it is possible to prevent the excessive gas state due to the foaming of the oil in the back pressure chamber 21 which is seen in the conventional configuration, to prevent the depletion of the oil in the compressor, and to surely supply the oil to the compression chamber.
  • oil that is compatible with the working fluid at a temperature of 50 ° C. or higher is discharged together with the discharge gas for some reason, even if a large amount of oil flows from the compressor to the refrigeration cycle. Easy to return to the compressor. For this reason, oil depletion of the compressor can be prevented.
  • the compatible oil has a property of foaming due to reduced pressure
  • the bypass discharge port 13 is The high-temperature discharged gas that has flowed back reaches the back pressure chamber 21 through the second path 24.
  • the temperature of the oil filled in the back pressure chamber 21 rises and foams, resulting in a further gas excess state.
  • the bypass discharge port 13 and the second path 24 do not communicate with the compression chamber 11 at the same time. For this reason, an excessive gas state due to foaming of the oil in the back pressure chamber 21 can be prevented. Therefore, the lubrication of the thrust bearing 26 and the sliding portions of the fixed scroll wrap 6b and the orbiting scroll wrap 9a can be realized by a good lubrication state, and the compression chamber can be reliably supplied with lubrication to the compression chamber 11. 11 can reduce the compression loss by the reliable seal.
  • Vb The volume of the compression chamber 11 at the time when the communication with the bypass discharge port 13 starts is defined as Va, and the volume of the compression chamber 11 at the time when the communication with the second path 24 ends with respect to this volume Va is defined as Vb. I do. These ratios Vb / Va should preferably be in the range of approximately 1 to 1.2.
  • the configuration is such that the bypass discharge port 13 and the second path 24 are brought as close as possible within a range where they do not communicate with the compression chamber 11 at the same time.
  • the pressure in the compression chamber 11 increases due to the oil supplied from the back pressure chamber 21 through the second path 24, and even if the compression chamber 11 is in an over-compressed state, the communication between the second path 24 and the compression chamber 11 is established.
  • the oil can be discharged from the bypass discharge port 13. For this reason, overcompression of the compression chamber 11 can be minimized, and a decrease in compressor efficiency can be suppressed.
  • Vb / Va exceeds 1.2, the effect of avoiding excessive compression by the bypass discharge port 13 under the low compression ratio operating condition is reduced, so that the compression power is increased and the efficiency of the compressor is likely to be reduced.
  • low-viscosity oil for example, low-viscosity oil such as viscosity grade 32
  • the sealing performance of the thrust bearing 26 cannot be maintained. Refrigerant leakage from the back pressure chamber 21 to the compression chamber 11 may occur, causing a decrease in performance. Therefore, when using a low-viscosity oil, the configuration of the present disclosure exerts more effects.
  • the two bottom counterbore 25 (the first bottom counterbore 25a and the second bottom counterbore 25b) are provided so as to communicate with the first compression chamber 11a and the second compression chamber 11b, respectively.
  • the same effect can be obtained even if only one bottom counterbore 25 is provided so as to communicate with one of the first compression chamber 11a and the second compression chamber 11b.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne un compresseur à spirale comprenant une spirale fixe (6), une spirale tournante (9), une chambre de compression (11) formée en engrenant ensemble la spirale fixe et la spirale tournante, et une région de haute pression et une chambre de contre-pression formées sur la surface arrière de la spirale tournante (9). Du fait de la rotation de la spirale tournante (9), la chambre de compression (11) se déplace vers le centre tout en changeant de capacité. Le compresseur à spirale comprend en outre un orifice de refoulement principal (12) disposé sur la partie centrale de la spirale fixe (6), un orifice de refoulement de dérivation (13) disposé sur la spirale fixe (6) de façon à communiquer avec la chambre de compression (11) à mi-chemin par compression, un premier canal (23) par le biais duquel la région haute pression et la chambre de contre-pression communiquent, et un deuxième canal (24) par le biais duquel la chambre de contre-pression et la chambre de compression communiquent par intermittence. Le compresseur à spirale est configuré de telle sorte que du fait de la rotation de la spirale tournante (9), la communication du deuxième canal (24) se termine avant que l'orifice de refoulement de dérivation (13) et la chambre de compression (11) communiquent.
PCT/JP2019/024576 2018-07-06 2019-06-20 Compresseur à spirale WO2020008902A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018-128651 2018-07-06
JP2018128651 2018-07-06

Publications (1)

Publication Number Publication Date
WO2020008902A1 true WO2020008902A1 (fr) 2020-01-09

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PCT/JP2019/024576 WO2020008902A1 (fr) 2018-07-06 2019-06-20 Compresseur à spirale

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011027076A (ja) * 2009-07-29 2011-02-10 Panasonic Corp スクロール圧縮機
JP2011102579A (ja) * 2009-10-14 2011-05-26 Panasonic Corp スクロール圧縮機
JP2011256819A (ja) * 2010-06-11 2011-12-22 Panasonic Corp スクロール圧縮機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011027076A (ja) * 2009-07-29 2011-02-10 Panasonic Corp スクロール圧縮機
JP2011102579A (ja) * 2009-10-14 2011-05-26 Panasonic Corp スクロール圧縮機
JP2011256819A (ja) * 2010-06-11 2011-12-22 Panasonic Corp スクロール圧縮機

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