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WO2025204084A1 - Compresseur à spirale - Google Patents

Compresseur à spirale

Info

Publication number
WO2025204084A1
WO2025204084A1 PCT/JP2025/002630 JP2025002630W WO2025204084A1 WO 2025204084 A1 WO2025204084 A1 WO 2025204084A1 JP 2025002630 W JP2025002630 W JP 2025002630W WO 2025204084 A1 WO2025204084 A1 WO 2025204084A1
Authority
WO
WIPO (PCT)
Prior art keywords
scroll
discharge
discharge chamber
case
passage
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.)
Pending
Application number
PCT/JP2025/002630
Other languages
English (en)
Japanese (ja)
Inventor
山下勝巳
管原彬人
本田和也
小林裕之
橋本友次
武藤圭史朗
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Industries Corp
Original Assignee
Toyota Industries Corp
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.)
Filing date
Publication date
Priority claimed from JP2024133803A external-priority patent/JP2025149788A/ja
Application filed by Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of WO2025204084A1 publication Critical patent/WO2025204084A1/fr
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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

Definitions

  • the present invention relates to a scroll compressor.
  • Patent Document 1 discloses a conventional scroll-type compressor (hereinafter simply referred to as a compressor).
  • This compressor comprises a housing, a drive mechanism, a first scroll, a second scroll, and a driven mechanism.
  • the drive mechanism and first scroll are housed within the housing.
  • the housing also has a boss that protrudes toward the first scroll.
  • a support hole and a discharge communication port are formed inside the boss.
  • the support hole is formed with a larger diameter than the discharge communication port, and is connected to the discharge communication port.
  • the discharge communication port is connected to the outside of the housing.
  • a drive shaft is formed on the first scroll.
  • the drive shaft is cylindrical and houses a boss inside.
  • a bearing is provided between the drive shaft and the boss, more specifically, between the inner peripheral surface of the drive shaft and the outer peripheral surface of the boss.
  • the outer peripheral surface of the drive shaft is fixed to the drive mechanism. In this way, the first scroll is fixed to the drive mechanism within the housing and is supported by the boss via the bearing so that it can rotate around the center of the drive shaft.
  • the second scroll is housed within the first scroll. This forms a compression chamber between the second scroll and the first scroll.
  • the second scroll also has a driven shaft that protrudes toward the boss. The driven shaft is inserted into the support hole. As a result, the second scroll is supported by the boss so that it can rotate around the driven axis while housed within the first scroll.
  • a discharge chamber is also formed inside the driven shaft. The discharge chamber is in communication with the compression chamber and also with the discharge communication port. In other words, the compression chamber and the discharge communication port are in communication through the discharge chamber.
  • the driven mechanism is disposed between the first scroll and the second scroll.
  • the first scroll is driven to rotate around the drive axis by the drive mechanism, and the driven scroll is driven to rotate around the driven axis by the first scroll and the driven mechanism.
  • the volume of the compression chamber changes depending on the rotationally driven first scroll and the rotationally driven second scroll.
  • refrigerant is sucked into the compression chamber and compressed.
  • the refrigerant compressed in the compression chamber is then discharged into the discharge chamber as compressed refrigerant, and is further discharged from the discharge chamber through the discharge connection port to the outside of the housing.
  • the refrigerant drawn into the compression chamber contains lubricating oil, and this lubricating oil is discharged from the compression chamber to the discharge chamber along with the compressed refrigerant. Therefore, it is believed that if such lubricating oil is used to lubricate the first scroll, second scroll, etc., the first scroll, second scroll, etc. can be suitably lubricated.
  • the scroll compressor of the present invention includes a housing, a drive mechanism, a first scroll, and a second scroll, the drive mechanism, the first scroll, and the second scroll are housed in the housing;
  • a scroll compressor in which a compression chamber for compressing a refrigerant is formed by the first scroll and the second scroll,
  • the housing is formed with a discharge port for discharging the compressed refrigerant, which is the refrigerant compressed in the compression chamber, to the outside.
  • a case is fixed to at least one of the first scroll, the second scroll, and the drive mechanism so as to be rotatable within the housing;
  • the case includes a discharge chamber that communicates with the compression chamber and into which the compressed refrigerant is discharged from the compression chamber.
  • a discharge passage communicating with the discharge chamber and the discharge communication port is formed;
  • a collision wall is provided within the discharge chamber, which rotates together with the case and collides with the compressed refrigerant flowing toward the discharge passage, thereby separating the lubricating oil contained in the compressed refrigerant from the compressed refrigerant.
  • a case is fixed to the first scroll, second scroll, or drive mechanism, and is rotatable within the housing.
  • a discharge chamber is formed within the case, and compressed refrigerant, which is refrigerant compressed in the compression chamber, is discharged into this discharge chamber.
  • the compressed refrigerant discharged into the discharge chamber contains lubricating oil.
  • a collision wall is provided within the discharge chamber.
  • This collision wall rotates with the case and collides with the compressed refrigerant flowing toward the discharge passage.
  • the lubricating oil contained in the compressed refrigerant can be separated from the compressed refrigerant by the compressed refrigerant colliding with the collision wall.
  • the centrifugal force of the rotating case acts on the compressed refrigerant discharged into the discharge chamber. This also allows the compressor to separate the lubricating oil contained in the compressed refrigerant from the compressed refrigerant.
  • the scroll compressor of the present invention has excellent durability.
  • the first scroll can be driven to rotate around the drive axis by the drive mechanism.
  • the second scroll can be driven to rotate around the driven axis by the first scroll and the driven mechanism while being eccentric with respect to the first scroll.
  • the case can be fixed to the first scroll. It is preferable that the first scroll be formed with a discharge port that communicates with the compression chamber.
  • the first scroll is rotationally driven and the second scroll is rotationally driven, so the compressor of the present invention becomes a double-rotating scroll compressor in which both the first and second scrolls rotate. Furthermore, because the case is fixed to the first scroll, the case can rotate favorably in conjunction with the rotational drive of the first scroll.
  • the collision wall may be plate-shaped and extend radially of the first scroll, and may have an opposing wall portion that faces the first scroll while being spaced apart from the first scroll in the drive shaft direction, and a connecting peripheral wall portion that connects to the opposing wall portion and extends cylindrically in the drive shaft direction.
  • the discharge chamber may be partitioned by the collision wall into a first discharge chamber and a second discharge chamber.
  • the first discharge chamber may be located between the collision wall and the first scroll, and may communicate with the discharge port.
  • the second discharge chamber may be located between the case and the collision wall, and may communicate with the discharge passage. It is preferable that the connecting peripheral wall portion have a communication passage that extends radially and connects the first discharge chamber and the second discharge chamber.
  • the compressed refrigerant collides with the opposing wall portion within the first discharge chamber, effectively separating the lubricating oil contained in the compressed refrigerant from the compressed refrigerant.
  • the collision wall may have a first surface facing the discharge valve in the drive shaft direction, and a second surface located opposite the first surface and abutting the case in the drive shaft direction.
  • the discharge passage may be covered by the collision wall while facing the second surface in the drive shaft direction. It is preferable that a radial flow path be formed between the second surface and the case, which guides the compressed refrigerant in the discharge chamber to the discharge passage while circulating it in the radial direction of the first scroll.
  • the case can be rotatably supported on the housing via a bearing. It is preferable that the discharge chamber be formed with a diameter larger than the outer diameter of the bearing.
  • the volume of the discharge chamber can be suitably secured, and the muffler effect of the discharge chamber can be used to suitably reduce discharge pulsation when compressed refrigerant is discharged into the discharge chamber.
  • this compressor can also reduce noise during operation.
  • the bearings are never larger in diameter than the discharge chamber, so the bearings can adequately support the case even when the case rotates at high speed within the housing.
  • the discharge chamber is preferably connected to a return passage that returns the lubricating oil in the discharge chamber to a location in the housing where the pressure is lower than that of the discharge chamber.
  • the lubricating oil separated from the compressed refrigerant can be used to lubricate the first scroll, second scroll, drive mechanism, etc.
  • the scroll compressor of the present invention has excellent durability.
  • FIG. 1 is a cross-sectional view of a scroll compressor according to a first embodiment.
  • FIG. 2 is a cross-sectional view of a scroll compressor according to a second embodiment.
  • FIG. 3 is a cross-sectional view of a scroll compressor according to a third embodiment.
  • FIG. 4 is a cross-sectional view of a scroll compressor according to a fourth embodiment.
  • FIG. 5 is a cross-sectional view showing a scroll compressor according to a fourth embodiment, taken along line AA in FIG.
  • FIG. 6 is a cross-sectional view of a scroll compressor according to a fifth embodiment.
  • FIG. 7 is a cross-sectional view similar to FIG. 5, showing a scroll compressor of a comparative example.
  • Embodiments 1 to 5 of the present invention will be described below with reference to the drawings.
  • the compressors in embodiments 1 to 5 are specifically double-rotating scroll compressors, and are mounted on a vehicle (not shown).
  • the compressor of Example 1 includes a housing 6, a drive mechanism 10, a first scroll 30, a second scroll 40, a driven mechanism 20, and a case 25.
  • the front-to-rear direction of the compressor is defined by the solid arrow shown in Figure 1. Note that the front-to-rear direction is an example for ease of explanation, and the compressor's position can be changed as appropriate depending on the vehicle in which it is installed. The same applies to the compressor shown in Figure 2.
  • the housing 6 is composed of a housing body 60 and a housing cover 61.
  • the housing body 60 and housing cover 61 are made of an aluminum alloy.
  • the housing body 60 is a bottomed, cylindrical member having an outer peripheral wall 60a and a rear wall 60b.
  • the outer peripheral wall 60a is cylindrical and centered on the drive axis O1.
  • the drive axis O1 is parallel to the front-to-rear direction.
  • An intake communication port 69 is formed in the outer peripheral wall 60a.
  • the intake communication port 69 penetrates the outer peripheral wall 60a in the radial direction of the housing body 60.
  • a pipe (not shown) is connected to the intake communication port 69.
  • the intake communication port 69 is connected to the outside of the housing 6, i.e., the outside of the compressor, via the pipe.
  • the rear wall 60b is located at the rear end of the housing main body 60.
  • the rear wall 60b extends in a generally circular, flat plate shape perpendicular to the drive axis O1.
  • the outer peripheral edge of the rear wall 60b is connected to the rear end of the outer peripheral wall 60a.
  • a first support portion 64 is formed at the center of the inner surface of the rear wall 60b.
  • the first support portion 64 is generally cylindrical and centered on the drive axis O1, and protrudes forward from the center of the inner surface of the rear wall 60b, i.e., into the scroll chamber 65 described below.
  • An intake communication port 69 may also be formed in the rear wall 60b.
  • a pin hole 54 is formed in the first support portion 64.
  • the pin hole 54 opens to the front end surface of the first support portion 64 and extends linearly rearward within the first support portion 64. Note that the pin hole 54 does not pass through the first support portion 64 in the front-to-rear direction.
  • the housing cover 61 is positioned in front of the housing main body 60.
  • the housing cover 61 extends in a generally circular, flat plate shape perpendicular to the drive axis O1.
  • the housing cover 61 is fixed to the housing main body 60 by bolts (not shown) with its outer edge abutting the front end of the outer peripheral wall 60a of the housing main body 60. In this way, the housing cover 61 closes the housing main body 60 from the front.
  • a scroll chamber 65 is thus formed within the housing main body 60.
  • a second support portion 67 is formed in the center of the inner surface of the housing cover 61.
  • the second support portion 67 is cylindrical and centered on the drive axis O1, and protrudes rearward from the center of the inner surface of the housing cover 61.
  • a radial ball bearing 14 and a shaft seal member 63 are provided within the second support portion 67.
  • the radial ball bearing 14 is an example of a "bearing” in the present invention.
  • the outer diameter of the radial ball bearing 14 is a first length L1, which is smaller than the outer diameter of the second support portion 67.
  • the radial ball bearing 14 is fixed to the second support portion 67 by fitting its outer ring into the second support portion 67. Note that a sliding bearing or the like may also be used as a "bearing" in the present invention.
  • the shaft seal member 63 is located in the second support portion 67, in front of the radial ball bearing 14.
  • the shaft seal member 63 is formed in an annular shape.
  • a discharge communication port 68 is also formed in the housing cover 61.
  • the discharge communication port 68 is located in the center of the housing cover 61 and penetrates the housing cover 61 in the direction of the drive axis O1.
  • the discharge communication port 68 faces the discharge passage 251 (described below) in the direction of the drive axis O1.
  • a pipe (not shown) is connected to the discharge communication port 68. As a result, the discharge communication port 68 is connected to the outside of the compressor via the pipe.
  • the scroll chamber 65 is connected to the suction port 69. As a result, low-pressure refrigerant is drawn into the scroll chamber 65 from outside the compressor through a pipe connected to the suction port 69. As a result, the scroll chamber 65 also functions as a refrigerant suction chamber.
  • the drive mechanism 10 is specifically an electric motor and is housed within the scroll chamber 65.
  • the scroll chamber 65 also serves as a motor chamber that houses the drive mechanism 10.
  • the drive mechanism 10 is composed of a stator 17 and a rotor 11.
  • the stator 17 has a stator core 17a and coil ends 17b.
  • the stator core 17a is cylindrical and centered on the drive axis O1.
  • the coil ends 17b are formed by part of the coil wound around the stator core 17a and have an annular shape that protrudes from the stator core 17a in the direction of the drive axis O1.
  • the stator 17 is fixed to the housing main body 60 by fitting the stator core 17a into the inner surface of the outer wall 60a.
  • the rotor 11 is cylindrical around the drive axis O1 and is disposed within the stator 17. Although detailed illustrations are omitted, the rotor 11 is composed of multiple permanent magnets corresponding to the stator 17 and multiple electromagnetic steel plates that secure each permanent magnet.
  • the first scroll 30 is made of an aluminum alloy.
  • the first scroll 30 is housed in the scroll chamber 65.
  • the first scroll 30 has a first end plate 31, a peripheral wall 32, a first spiral body 33, and a cover body 35.
  • the first end plate 31 extends in a generally circular plate shape, perpendicular to the drive axis O1 and the driven axis O2.
  • the driven axis O2 extends parallel to the drive axis O1 while being eccentric relative to the drive axis O1.
  • the driven axis O2 is also parallel to the front-to-rear direction.
  • the first end plate 31 has a front surface 311 and a rear surface 312 located opposite the front surface 311.
  • the first end plate 31 also has an outlet port 38 formed therein.
  • the outlet port 38 is located approximately in the center of the first end plate 31 and penetrates the first end plate 31 in the direction of the drive axis O1.
  • a discharge reed valve 57 and a retainer 58 are fixed to the front surface 311 of the first end plate 31 with fixing bolts 59.
  • the discharge reed valve 57 is an example of the "discharge valve" in the present invention. This allows the discharge reed valve 57 to open and close the discharge port 38.
  • the retainer 58 is also capable of adjusting the opening degree of the discharge reed valve 57.
  • the peripheral wall 32 is formed in a cylindrical shape centered on the drive axis O1 and extending parallel to the drive axis O1 and the driven axis O2.
  • the front end of the peripheral wall 32 is integral with the outer peripheral edge of the first end plate 31, and the peripheral wall 32 extends cylindrically rearward from the first end plate 31.
  • peripheral wall 32 is inserted into the rotor 11 and fixed to the inner peripheral surface of the rotor 11. This integrates the peripheral wall 32 and the rotor 11.
  • the first spiral body 33 is disposed inside the peripheral wall 32.
  • the first spiral body 33 is integral with the first end plate 31 and extends rearward from the rear surface 312 of the first end plate 31, i.e., toward the second scroll 40, parallel to the drive axis O1 and the driven axis O2.
  • the first spiral body 33 extends spirally from the center of the spiral toward the outer periphery, with the center of the spiral being on the central side of the first end plate 31.
  • the outer peripheral end of the spiral of the first spiral body 33 is connected to the inner peripheral surface of the peripheral wall 32.
  • the cover body 35 extends in a generally circular plate shape, perpendicular to the drive axis O1 and the driven axis O2.
  • the cover body 35 is formed to have roughly the same diameter as the first end plate 31 and the peripheral wall 32.
  • the cover body 35 has a front surface 351 and a rear surface 352.
  • the front surface 351 faces the rear surface 312 of the first end plate 31.
  • the rear surface 352 is located on the opposite side of the front surface 351 and faces the rear wall 60b of the housing main body 60.
  • the cover body 35 also has a boss 36, an intake port 35a, and multiple second mounting holes 353.
  • the boss 36 is formed integrally with the center of the cover body 35 and protrudes rearward from the rear surface 352.
  • the boss 36 also has an insertion hole 350.
  • the insertion hole 350 penetrates through the boss 36 and the cover body 35 in the direction of the drive axis O1. This gives the boss 36 a cylindrical shape centered on the drive axis O1.
  • a plain bearing 51 is provided within the insertion hole 350. Note that a ball bearing or the like may be provided within the insertion hole 350 instead of the plain bearing 51.
  • Each second mounting hole 353 is positioned radially outward of the cover body 35 relative to the suction port 35a. Each second mounting hole 353 penetrates the cover body 35 in the direction of the drive axis O1.
  • a plurality of rings 22 are attached to the cover body 35 between the boss 36 and the intake port 35a.
  • the rings 22 are arranged at equal intervals around the circumferential direction of the cover body 35 while facing forward, and surround the boss 36 and insertion hole 350 from the outside.
  • Figure 1 shows two of the six rings 22. The same applies to Figure 2.
  • a collision cylinder 71 is fixed to the first scroll 30. More specifically, the collision cylinder 71 is fixed to the first end plate 31.
  • the collision cylinder 71 is an example of a "collision wall" in the present invention.
  • the collision cylinder 71 is made of an aluminum alloy.
  • the collision cylinder 71 has an opposing wall portion 71a and a connecting peripheral wall portion 71b.
  • the collision cylinder 71 may also be made of resin.
  • the opposing wall portion 71a is located at the front end of the collision cylinder 71.
  • the opposing wall portion 71a extends in a generally circular, flat plate shape perpendicular to the drive axis O1.
  • the opposing wall portion 71a has a first surface 711 and a second surface 712.
  • the first surface 711 is an example of the "first surface” in the present invention.
  • the second surface 712 is an example of the "second surface” in the present invention.
  • the first surface 711 faces rearward.
  • the second surface 712 is located on the opposite side of the first surface 711 in the direction of the drive axis O1 and faces forward.
  • the opposing wall portion 71a is formed with a smaller diameter than the first end plate 31.
  • the connecting peripheral wall portion 71b is cylindrical, centered on the drive axis O1, and extends cylindrically in the direction of the drive axis O1.
  • the connecting peripheral wall portion 71b has an inner diameter the same as that of the opposing wall portion 71a.
  • the connecting peripheral wall portion 71b is connected at its front end to the outer periphery of the opposing wall portion 71a.
  • the opposing wall portion 71a and the connecting peripheral wall portion 71b give the collision cylinder 71 a cylindrical shape with a bottom and an open rear.
  • a flange 710 and multiple lubricating oil passages 73 are formed in the connecting peripheral wall portion 71b.
  • the flange 710 is located at the rear end of the connecting peripheral wall portion 71b and protrudes outward in the radial direction of the collision cylinder 71. This gives the flange 710 the largest diameter in the collision cylinder 71.
  • a plurality of first mounting holes 713 are formed in the flange 710. Each of the first mounting holes 713 penetrates the flange 710 in the direction of the drive axis O1.
  • the opposing wall portion 71a of the collision cylinder 71 is spaced forward of the first end plate 31 by the length of the connecting peripheral wall portion 71b in the front-to-rear direction, and faces the front surface 311 of the first end plate 31 in the front-to-rear direction.
  • a first discharge chamber 16a is formed inside the collision cylinder 71, i.e., between the opposing wall portion 71a, the connecting peripheral wall portion 71b, and the front surface 311 of the first end plate 31.
  • the discharge port 38 is located within this first discharge chamber 16a and is in communication with the first discharge chamber 16a.
  • the discharge reed valve 57 and retainer 58 fixed to the front surface 311 by the fixing bolt 59 are also located within the first discharge chamber 16a.
  • the discharge port 38, discharge reed valve 57, retainer 58, and fixing bolt 59 face, but are spaced apart from, the first surface 711 of the opposing wall portion 71a in the direction of the drive axis O1.
  • the second scroll 40 is also made of an aluminum alloy.
  • the second scroll 40 is housed within the scroll chamber 65, more specifically, within the first scroll 30.
  • the second scroll 40 has a second end plate 41 and a second spiral body 43.
  • the second end plate 41 extends in a generally circular plate shape, perpendicular to the drive axis O1 and the driven axis O2.
  • the second end plate 41 has a front surface 411 and a rear surface 412.
  • the front surface 411 faces the rear surface 312 of the first end plate 31 within the first scroll 30.
  • the rear surface 412 is located on the opposite side of the front surface 411 and faces the front surface 351 of the cover body 35.
  • a housing portion 41a is formed in the second end plate 41.
  • the housing portion 41a is recessed in a cylindrical shape centered on the driven axis O2 from the rear surface 412 of the second end plate 41 toward the front.
  • a bushing 53 is provided within the housing portion 41a. Note that the bushing 53 may be provided within the housing portion 41a via a plain bearing, ball bearing, etc.
  • a driven pin 55 is inserted into the bushing 53.
  • the driven pin 55 is inserted into the bushing 53 at a position eccentric to the center of the bushing 53, i.e., the driven axis O2.
  • the driven pin 55 is made of steel and has a cylindrical shape. The driven pin 55 protrudes rearward from the bushing 53 and, therefore, from the second end plate 41.
  • a plurality of rotation prevention pins 21 are fixed on the outer periphery of the accommodating portion 41a, protruding rearward from the rear surface 412. More specifically, each rotation prevention pin 21 is fixed on the outer periphery of the accommodating portion 41a, at a location facing the ring 22. As a result, the rotation prevention pins 21 are arranged at equal intervals around the circumferential direction of the second end plate 41, and surround the accommodating portion 41a and bushing 53 from the outside.
  • the number of rotation prevention pins 21 is six, corresponding to the number of rings 22. Also, two of the six rotation prevention pins 21 are shown in Figures 1 and 2.
  • the second spiral body 43 is integral with the second end plate 41 and extends forward from the front surface 411 of the second end plate 41, i.e., toward the first end plate 31, parallel to the drive axis O1 and the driven axis O2. Although detailed illustration is omitted, the second spiral body 43 extends spirally from the spiral center toward the outer periphery, with the center of the spiral being on the central side of the second end plate 41.
  • the driven mechanism 20 is composed of the aforementioned rotation-preventing pins 21 and rings 22. Note that the number of rotation-preventing pins 21 and rings 22 constituting the driven mechanism 20 can be changed as appropriate, as long as there are three or more of each.
  • the case 25 is a bottomed cylindrical member having a case peripheral wall 25a and a case bottom wall 25b.
  • the case 25 is made of an aluminum alloy.
  • the case peripheral wall 25a is cylindrical and centered on the drive axis O1.
  • the outer diameter of the case peripheral wall 25a is approximately the same as the first end plate 31.
  • the inner diameter of the case peripheral wall 25a is approximately the same as the outer diameter of the flange 710 of the connecting peripheral wall portion 71b. More specifically, the length of the inner diameter of the case peripheral wall 25a is a second length L2. This second length L2 is longer than the first length L1, which is the length of the outer diameter of the radial ball bearing 14. Therefore, the inner diameter of the case peripheral wall 25a is larger than the outer diameter of the radial ball bearing 14.
  • the case 25 may also be made of resin.
  • third mounting holes 253 are formed in the case peripheral wall 25a.
  • the return flow path 250 penetrates the case peripheral wall 25a in the radial direction of the case 25.
  • Each of the third mounting holes 253 penetrates the case peripheral wall 25a in the direction of the drive axis O1.
  • the return flow path 250 and each of the third mounting holes 253 are formed in different positions on the case peripheral wall 25a. Therefore, the return flow path 250 and each of the third mounting holes 253 are not in communication with each other.
  • Case bottom wall 25b is located at the front end of case 25 and extends in a generally circular, flat plate shape perpendicular to drive axis O1.
  • Case bottom wall 25b has a front surface 255 and a rear surface 256.
  • the front surface 255 faces forward.
  • the rear surface 256 is located on the opposite side of the front surface 255 in the direction of drive axis O1 and faces rearward.
  • the outer peripheral edge of case bottom wall 25b is connected to the front end of case peripheral wall 25a.
  • case bottom wall 25b is formed with a boss 25c.
  • Boss 25c is formed integrally with the center of case bottom wall 25b and protrudes forward from the front surface 255.
  • Boss 25c is formed with a diameter generally equal to the inner diameter of radial ball bearing 14 and the inner diameter of shaft seal member 63.
  • a discharge passage 251 is formed within boss 25c.
  • Discharge passage 251 penetrates boss 25c and case bottom wall 25b in the direction of drive axis O1.
  • the front end of discharge passage 251 opens to the front end face of boss 25c
  • the rear end of discharge passage 251 opens to the rear face 256 of case bottom wall 25b. This gives boss 25c a cylindrical shape centered on drive axis O1.
  • each rotation-prevention pin 21 is inserted into each ring 22, and the front surface 351 of the cover body 35 is abutted against the rear end of the peripheral wall 32.
  • second fixing bolts 50b are inserted into each second mounting hole 353, and the cover body 35 is fixed to the rear end of the peripheral wall 32 by each second fixing bolt 50b.
  • first scroll 30 and the second scroll 40 are assembled in the front-to-rear direction while the second scroll 40 is housed within the first scroll 30.
  • first scroll 30 and the second scroll 40 form the scroll compression section 100.
  • the first scroll 30 and the second scroll 40 form the suction section 30a.
  • the first spiral body 33 and the second spiral body 43 are located within the suction section 30a.
  • the suction section 30a is separated from the scroll chamber 65 by the first end plate 31, the peripheral wall 32, and the cover body 35, and is also separated from the first discharge chamber 16a and the second discharge chamber 16b (described below) by the first end plate 31.
  • the suction section 30a is also connected to the suction port 35a.
  • the case 25 is fixed to the first scroll 30.
  • the case 25 has the rear end of the case peripheral wall 25a abutting against the front face 311 of the first end plate 31.
  • the rear end of the case peripheral wall 25a abuts against the front face 311 on the outer periphery side of the flange 710 of the collision cylinder 71.
  • the case 25 is fixed to the first end plate 31 by third fixing bolts 50c inserted into each third mounting hole 253. In this way, the case 25 is fixed to the first scroll 30 and is integrated with the first scroll 30.
  • the case peripheral wall 25a and case bottom wall 25b of the case 25 and the first end plate 31 form a discharge chamber 16 inside the case 25.
  • the discharge chamber 16 is in communication with the return flow path 250 and the discharge passage 251.
  • the length of the inner diameter of the case peripheral wall 25a is the second length L2, and therefore the length of the inner diameter of the discharge chamber 16 is also the second length L2.
  • the discharge chamber 16 is formed with a diameter larger than the outer diameter of the radial ball bearing 14.
  • the collision cylinder 71 is disposed within the discharge chamber 16.
  • the discharge chamber 16 is divided by the collision cylinder 71 into a first discharge chamber 16a and a second discharge chamber 16b.
  • the first discharge chamber 16a is formed between the opposing wall portion 71a and connecting peripheral wall portion 71b of the collision cylinder 71 and the front surface 311 of the first end plate 31.
  • the second discharge chamber 16b is formed by the case peripheral wall 25a and case bottom wall 25b of the case 25 and the collision cylinder 71.
  • the second discharge chamber 16b is located outside the first discharge chamber 16a.
  • the second surface 712 of the opposing wall portion 71a and the rear surface 256 of the case bottom wall 25b face each other while being spaced apart in the direction of the drive axis O1.
  • the first discharge chamber 16a and the second discharge chamber 16b are connected by respective lubricating oil passages 73.
  • each lubricating oil passage 73 penetrates the connecting peripheral wall portion 71b in the radial direction of the collision cylinder 71, so the first discharge chamber 16a and the second discharge chamber 16b are connected in the radial direction of the collision cylinder 71.
  • the second discharge chamber 16b is connected to the return flow path 250 and the discharge passage 251, respectively.
  • the boss 25c of the case 25 is fitted into the inner ring of the radial ball bearing 14 and is inserted into the shaft seal member 63.
  • the case 25 is supported rotatably around the drive axis O1 relative to the second support portion 67, i.e., the housing 6, via the radial ball bearing 14.
  • the discharge passage 251 faces the discharge communication port 68 from the rear. This allows communication between the second discharge chamber 16b, and therefore the discharge chamber 16, and the discharge communication port 68 through the discharge passage 251.
  • the shaft seal member 63 seals the discharge passage 251 and the discharge communication port 68 from the scroll chamber 65.
  • the first support portion 64 is inserted into the plain bearing 51, i.e., into the boss 36.
  • the cover body 35 is rotatably supported by the first support portion 64 via the plain bearing 51.
  • the suction port 35a faces the scroll chamber 65. In this way, the suction port 35a communicates between the scroll chamber 65 and the suction portion 30a.
  • the case 25 is rotatably supported by the second support portion 67. Therefore, the first scroll 30 is rotatably supported by the second support portion 67 via the case 25. As a result, the first scroll 30 is rotatably supported by the housing 6 around the drive axis O1 by both the first support portion 64 and the second support portion 67.
  • the driven pin 55 is inserted into the pin hole 54 of the first support portion 64.
  • the second scroll 40 is supported by the driven pin 55 on the first support portion 64 so as to be rotatable around the driven axis O2.
  • the second scroll 40 is supported on the housing 6 so as to be rotatable around the driven axis O2 only by the first support portion 64.
  • the driven axis O2 is eccentric with respect to the drive axis O1. Therefore, the second scroll 40 is supported by the housing 6 so as to be rotatable about the driven axis O2, and is housed within the first scroll 30 in an eccentric state with respect to the first scroll 30.
  • the second scroll 40 is rotated around the driven axis O2 by the first scroll 30 and the driven mechanism 20.
  • the driven mechanism 20 restricts the second scroll 40 from rotating on its own axis.
  • the second scroll 40 revolves around the driven axis O2 relative to the first scroll 30.
  • the first and second spiral bodies 33 and 43 each rotate within the suction section 30a, the first and second spiral bodies 33 and 43 form a compression chamber 12 between them.
  • low-pressure refrigerant is drawn into the scroll chamber 65 from outside the compressor through the piping and the suction port 69, as shown by the dashed arrow in Figure 1.
  • the refrigerant drawn into the scroll chamber 65 contains lubricating oil 18.
  • the refrigerant in this scroll chamber 65 is drawn into the compression chamber 12 through the suction port 35a and the suction section 30a.
  • the compression chamber 12 then compresses the refrigerant by reducing its volume while trapping the refrigerant within itself as the first scroll 30 rotates and the second scroll 40 rotates.
  • the refrigerant compressed to discharge pressure thus becomes high-pressure compressed refrigerant.
  • the discharge reed valve 57 then opens the discharge port 38, and the compressed refrigerant is discharged from the discharge port 38 into the first discharge chamber 16a. Therefore, the first discharge chamber 16a has a higher-pressure atmosphere than the scroll chamber 65 and the suction section 30a.
  • the compressed refrigerant discharged from the discharge port 38 into the first discharge chamber 16a flows from the first discharge chamber 16a into the discharge chamber 16 and further toward the discharge passage 251.
  • the compressed refrigerant discharged from the discharge port 38 into the first discharge chamber 16a contains lubricating oil 18. Then, as the compressed refrigerant in the first discharge chamber 16a heads toward the discharge chamber 16, it collides with the opposing wall 71a, more specifically, the first surface 711 of the opposing wall 71a. As a result, the opposing wall 71a separates the lubricating oil 18 contained in the compressed refrigerant from the compressed refrigerant. The lubricating oil 18 separated from the compressed refrigerant flows through each lubricating oil passage 73 and is discharged into the second discharge chamber 16b. The compressed refrigerant that collides with the opposing wall 71a also flows through each lubricating oil passage 73 and is discharged into the second discharge chamber 16b.
  • the compressed refrigerant discharged from the discharge port 38 into the first discharge chamber 16a collides with the opposing wall 71a before being discharged from the first discharge chamber 16a into the second discharge chamber 16b.
  • some of the compressed refrigerant discharged from the discharge port 38 into the first discharge chamber 16a can be discharged into the second discharge chamber 16b by flowing through each lubricating oil passage 73 before colliding with the opposing wall 71a.
  • most of the compressed refrigerant discharged from the discharge port 38 into the first discharge chamber 16a collides with the opposing wall 71a before being discharged from the first discharge chamber 16a into the second discharge chamber 16b.
  • the collision cylinder 71 rotates integrally with the first scroll 30 around the drive axis O1.
  • centrifugal force acts on the lubricating oil 18 that is separated from the discharged refrigerant when the discharged refrigerant collides with the opposing wall portion 71a.
  • the lubricating oil 18 in the first discharge chamber 16a flows radially outward from the collision cylinder 71.
  • each lubricating oil passage 73 radially penetrates the connecting peripheral wall portion 71b, the lubricating oil 18 in the first discharge chamber 16a is efficiently discharged into the second discharge chamber 16b by each lubricating oil passage 73.
  • the lubricating oil 18 and compressed refrigerant are discharged from the first discharge chamber 16a into the second discharge chamber 16b through each lubricating oil passage 73, so the second discharge chamber 16b also has a higher pressure atmosphere than the scroll chamber 65 and suction section 30a.
  • the scroll chamber 65 and suction section 30a have a lower pressure suction atmosphere than the first discharge chamber 16a and second discharge chamber 16b, i.e., the discharge chamber 16.
  • the case 25 also rotates integrally with the first scroll 30 around the drive axis O1. Therefore, the centrifugal force of the rotating case 25 causes the lubricating oil 18 discharged from each lubricating oil passage 73 into the second discharge chamber 16b to adhere to the inner surface of the case peripheral wall 25a, i.e., the inner circumferential surface of the second discharge chamber 16b, and also tends to remain within the second discharge chamber 16b at locations radially outward from the case 25. The centrifugal force of the case 25 also acts on the compressed refrigerant discharged from each lubricating oil passage 73 into the second discharge chamber 16b.
  • the compressed refrigerant in the second discharge chamber 16b i.e., the discharge chamber 16 is discharged to the outside of the housing 6 through the discharge passage 251 and the discharge communication port 68.
  • the compressed refrigerant can be discharged to the outside of the housing 6 while being separated from the lubricating oil 18, while the lubricating oil 18 can be effectively prevented from being discharged to the outside of the housing 6.
  • the collision cylinder 71 is arranged inside the case 25 with the front-to-rear direction reversed compared to Example 1.
  • the flange 710 of the connecting peripheral wall portion 71b is abutted against the case bottom wall 25b of the case 25, and the collision cylinder 71 is fixed to the case 25 by the first fixing bolt 50a.
  • the connecting peripheral wall portion 71b extends cylindrically rearward from the case bottom wall 25b in the direction of the drive axis O1.
  • a discharge passage 26d is formed within boss 26c.
  • Discharge passage 26d penetrates boss 26c and main body 265 in the direction of drive axis O1.
  • the front end of discharge passage 26d opens to the front end face of boss 26c
  • the rear end of discharge passage 26d opens to the rear surface 265b of main body 265 (see Figure 5). More specifically, the rear end of discharge passage 26d opens to the center of rear surface 265b.
  • boss 26c like boss 25c described above, has a cylindrical shape centered on drive axis O1, as shown in Figure 4.
  • the protrusions 266-269 are each integral with the main body 265 and protrude rearward from the rear surface 265b of the main body 265 toward the collision wall 91. Furthermore, as shown in Figure 5, the protrusions 266-269 are positioned radially outward of the case 26 relative to the discharge passage 26d, i.e., radially outward of the first scroll 30. The protrusions 266-269 are then arranged at equal intervals around the circumferential direction of the case 26 so as to surround the discharge passage 26d.
  • Protrusions 266-269 have the same shape and each have a tip portion 266a-269a.
  • tip portion 266a is the outermost portion of protrusion 266 in the radial direction of case 26, and is located at the tip-most position in the rotation direction R1 of case 26 and first scroll 30 (see white arrow in Figure 5).
  • the rear end of the case peripheral wall 26a of the case 26 abuts against the front surface 311 of the first end plate 31.
  • the case 26 is fixed to the first end plate 31 by third fixing bolts 50c inserted through each of the third mounting holes 263.
  • the case 26 is fixed to the first scroll 30 and is integrated with the first scroll 30.
  • a discharge chamber 19 is formed inside the case 26 by the case peripheral wall 26a and case bottom wall 26b of the case 26 and the first end plate 31.
  • the discharge chamber 19 is in communication with the compression chamber 12 through the discharge port 38.
  • the discharge chamber 19 is also in communication with the return flow path 260 and the discharge passage 26d.
  • the discharge chamber 19 is also formed with a diameter larger than the outer diameter of the radial ball bearing 14.
  • the collision wall 91 is formed in a circular plate shape that is perpendicular to the drive axis O1 and the driven axis O2.
  • the collision wall 91 is formed with a diameter larger than the discharge passage 26d, but smaller than the main body portion 265 of the case bottom wall 26b.
  • the collision wall 91 has a first surface 911 and a second surface 912.
  • the first surface 911 is also an example of the "first surface” in the present invention.
  • the second surface 912 is also an example of the "second surface” in the present invention.
  • the first surface 911 faces rearward.
  • the second surface 912 is located on the opposite side of the first surface 911 in the direction of the drive axis O1, and faces the case bottom wall 26b.
  • the collision wall 91 has its second surface 912 abutting against the protrusions 266-269. In this state, the collision wall 91 is fixed to the protrusions 266-269 by a plurality of fourth fixing bolts 50d. This allows the collision wall 91 to be integrated with the case 26.
  • the collision wall 91 is positioned within the discharge chamber 19.
  • the discharge port 38, discharge reed valve 57, retainer 58, and fixing bolt 59 face, but are spaced apart from, the first surface 911 of the collision wall 91 in the direction of the drive axis O1.
  • the discharge passage 26d faces the center of the second surface 912 of the collision wall 91 and is covered from the rear by the collision wall 91.
  • first to fourth radial flow paths 15a-15d are formed between the second surface 912 and the rear surface 265b of the main body 265, and also in the locations between the protrusions 266-269.
  • the first to fourth radial flow paths 15a-15d are an example of the "radial flow path" defined in the present invention.
  • the first radial flow passage 15a is located between the protruding portions 266 and 267 in the circumferential direction of the case 26, and the second radial flow passage 15b is located between the protruding portions 267 and 268 in the circumferential direction of the case 26.
  • the third radial flow passage 15c is located between the protruding portions 268 and 269 in the circumferential direction of the case 26, and the fourth radial flow passage 15d is located between the protruding portions 269 and 266 in the circumferential direction of the case 26.
  • first radial flow passage 15a, the second radial flow passage 15b, the third radial flow passage 15c, and the fourth radial flow passage 15d are arranged at equal intervals in this order in the rotation direction R1 of the case 26 and the first scroll 30.
  • the first to fourth radial flow paths 15a to 15d all have the same shape and extend radially of the first scroll 30 toward the discharge passage 26d, that is, from the center of the collision wall 91 toward the outer periphery of the collision wall 91.
  • the first to fourth radial flow paths 15a to 15d each connect the discharge passage 26d to the discharge chamber 19 in the radial direction of the first scroll 30.
  • first to fourth radial flow paths 15a to 15d each have an inlet portion 151, an upstream passage portion 152, and a downstream passage portion 153.
  • inlet portion 151, upstream passage portion 152, and downstream passage portion 153 will be explained based on the first radial flow path 15a.
  • the inlet portion 151 is located at the outermost position in the radial direction of the first scroll 30 in the first radial flow path 15a.
  • the inlet portion 151 opens into the discharge chamber 19. In this way, the inlet portion 151 connects the first radial flow path 15a to the inside of the discharge chamber 19.
  • the upstream passage section 152 is located radially inward of the inlet section 151 of the first scroll 30 and is connected to the inlet section 151.
  • the upstream passage section 152 extends from the inlet section 151 side toward the discharge passage 26d side, that is, from the inlet section 151 side toward the downstream passage section 153 side, while inclining in the opposite direction to the rotation direction R1 of the first scroll 30.
  • the downstream passage section 153 is located radially inward of the upstream passage section 152 in the radial direction of the first scroll 30.
  • the downstream passage section 153 connects to the discharge passage 26d at the radially innermost point of the first scroll 30, that is, at the point toward the center of the collision wall 91.
  • the downstream passage section 153 extends radially from the discharge passage 26d side toward the upstream passage section 152 in the radial direction of the first scroll 30, and connects to the upstream passage section 152 on the side opposite the inlet section 151.
  • the downstream passage section 153 extends linearly from the discharge passage 26d side in the radial direction of the first scroll 30, then curves toward the upstream passage section 152 and connects to the upstream passage section 152.
  • the remaining configuration of this compressor is the same as that of the compressor of Example 1.
  • the drive mechanism 10 drives the first scroll 30 and case 26 to rotate around the drive axis O1 in the rotational direction R1 shown in Figure 5.
  • the discharge reed valve 57 opens the discharge port 38, causing the compressed refrigerant compressed in the compression chamber 12 to be discharged from the discharge port 38 into the discharge chamber 19.
  • the discharge chamber 19 has a higher pressure atmosphere than the scroll chamber 65 and the suction section 30a.
  • the collision wall 91 is fixed to the protrusions 266-269, so that the discharge passage 26d is covered from the rear by the collision wall 91. Therefore, most of the compressed refrigerant flowing through the discharge chamber 19 toward the discharge passage 26d collides with the first surface 911 of the collision wall 91. In this way, the collision wall 91 separates the lubricating oil 18 contained in the compressed refrigerant from the compressed refrigerant.
  • the lubricating oil 18 separated from the compressed refrigerant flows radially outward within the discharge chamber 19 due to centrifugal force.
  • the lubricating oil 18 is more likely to adhere to the inner surface of the discharge chamber 19, making it more likely for the lubricating oil 18 to remain within the discharge chamber 19.
  • the lubricating oil 18 in the discharge chamber 19 also flows into the scroll chamber 65 through the return path 260. In this way, in this compressor as well, the lubricating oil 18 that flows into the scroll chamber 65 can lubricate the drive mechanism 10, radial ball bearing 14, sliding bearing 51, etc.
  • the compressed refrigerant from which the lubricating oil 18 has been separated upon collision with the collision wall 91 flows from the radial outside of the first scroll 30 around to the front of the collision wall 91, and reaches the first to fourth radial flow paths 15a to 15d.
  • This compressed refrigerant then flows through the first to fourth radial flow paths 15a to 15d, and is guided to the discharge passage 26d.
  • the compressed refrigerant flows through the inlet portion 151, the upstream passage portion 152, and the downstream passage portion 153 in that order, thereby guiding the compressed refrigerant to the discharge passage 26d. In this way, the compressed refrigerant is discharged to the outside of the housing 6 via the discharge passage 26d and the discharge communication port 68.
  • this compressor In this compressor, some of the lubricating oil 18 present in the discharge chamber 19 will inevitably flow toward the first to fourth radial flow paths 15a to 15d along with the compressed refrigerant. However, this compressor is able to effectively prevent the lubricating oil 18 from being discharged to the outside of the housing 6 via the discharge passage 26d along with the compressed refrigerant. This effect will be explained below in comparison with a comparative example.
  • the case bottom wall 26b has protrusions 97a to 97d.
  • the collision wall 91 is fixed to the protrusions 97a to 97d, thereby forming first to fourth radial flow paths 98a to 98d between the second surface 912 of the collision wall 91 and the rear surface 265b of the main body portion 265, and in locations between the protrusions 97a to 97d.
  • the first to fourth radial flow paths 98a to 98d each have an inlet portion 981, an upstream passage portion 982, and a downstream passage portion 983.
  • the upstream passage portion 982 extends from the inlet portion 981 side toward the discharge passage 26d side while inclining in the same direction as the rotation direction R1 of the first scroll 30.
  • the other configurations of the compressor of the comparative example, including the configurations of the inlet portion 981 and the downstream passage portion 983, are the same as those of the compressor of Example 4.
  • the compressed refrigerant and lubricating oil 18 rotating in the rotational direction R1 can flow smoothly from the inlet portion 981 to the upstream passage portion 982.
  • the compressor of the comparative example not only the compressed refrigerant but also the lubricating oil 18 can easily flow through the first to fourth radial flow paths 98a to 98d.
  • the flow rate of the lubricating oil 18 discharged to the outside of the housing 6 via the discharge passage 26d together with the compressed refrigerant is inevitably high.
  • the compressed refrigerant can flow through the first to fourth radial flow paths 15a to 15d and reach the discharge passage 26d, but the lubricating oil 18 has difficulty flowing through the first to fourth radial flow paths 15a to 15d and therefore is unlikely to reach the discharge passage 26d.
  • the compressor of Example 4 it is possible to effectively prevent the lubricating oil 18 from being discharged to the outside of the housing 6 via the discharge passage 26d along with the compressed refrigerant.
  • the downstream passage portion 153 curves toward the upstream passage portion 152 and connects to the upstream passage portion 152. Therefore, in this compressor, when the compressed refrigerant flows through the first to fourth radial flow paths 15a to 15d toward the discharge passage 26d, the flow resistance of the compressed refrigerant between the upstream passage portion 152 and the downstream passage portion 153 can be minimized. As a result, in this compressor, it is possible to effectively suppress pressure loss of the compressed refrigerant that flows through the first to fourth radial flow paths 15a to 15d and reaches the discharge passage 26d. Other functions of this compressor are the same as those of the compressor in Example 1.
  • the compressor of Example 5 has the same configuration as the compressor of Example 1, except that it has case 26 instead of case 25.
  • the collision cylinder 71 divides the discharge chamber 19 into a first discharge chamber 19a and a second discharge chamber 19b.
  • the discharge passage 26d is covered from the rear by the collision cylinder 71, facing the center of the second surface 712 of the opposing wall portion 71a. Furthermore, in this compressor, the opposing wall portion 71a abuts against the protrusions 266-269, thereby forming first to fourth radial flow paths 15a-15d between the second surface 712 of the opposing wall portion 71a and the rear surface 265b of the main body portion 265, and also between the protrusions 266-269 (FIG. 6 shows the first and third radial flow paths 15a and 15c; see FIG. 5 for the second and fourth radial flow paths 15b and 15d).
  • this compressor the compressed refrigerant collides with the first surface 711 of the opposing wall portion 71a in the first discharge chamber 19a, separating the lubricating oil 18 from the compressed refrigerant.
  • This compressed refrigerant is then discharged into the second discharge chamber 16b, flows through the first to fourth radial flow paths 15a to 15d, and is then discharged to the outside of the housing 6 via the discharge passage 26d and the discharge communication port 68.
  • this compressor is able to perform the functions of both the compressor of Example 1 and the compressor of Example 4.
  • the collision cylinder 71 fixed to the first end plate 31 is the "collision wall" of the present invention.
  • this is not limited to this, and a plate-like collision wall extending into the discharge chamber 16 may be provided on the case peripheral wall 25a of the case 25, so that the compressed refrigerant discharged from the discharge port 38 into the discharge chamber 16 collides against this collision wall.
  • a plate-like collision wall extending into the discharge chamber 16 may be provided on the case peripheral wall 25a of the case 25, so that the compressed refrigerant discharged from the discharge port 38 into the discharge chamber 16 collides against this collision wall.
  • the compressor of Example 2 the same applies to the compressor of Example 2.
  • the return flow path 250 is formed in the case peripheral wall 25a of the case 25.
  • the return flow path 250 may be formed in the first end plate 31 and the peripheral wall 32.
  • the return flow path 250 may return the lubricating oil 18 in the discharge chamber 16 to a location such as between the front surface 351 of the cover body 35 and the rear surface 412 of the second end plate 41. The same applies to the compressor of Example 2.
  • the collision cylinder 71 is fixed to the first end plate 31 by the first fixing bolt 50a.
  • the flange 710 of the connecting peripheral wall portion 71b may be inserted between the case peripheral wall 25a of the case 25 and the first end plate 31, and the case 25 and collision cylinder 71 may be fixed to the first end plate 31 by the third fixing bolt 50c.
  • the rotor 11 may be fixed to the case peripheral wall 25a of the case 25, so that the rotation of the rotor 11 is transmitted to the first scroll 30 by the case 25.
  • the first scroll 30 and the rotor 11 may be connected by a shaft so that power can be transmitted between them, thereby disposing the first scroll 30 and the case 25 and the rotor 11 at a distance from each other in the direction of the drive axis O1.
  • the first scroll 30 may be fixed to the housing 6, and the second scroll 40 may revolve relative to the first scroll 30.
  • the collision cylinder 71 has a connecting peripheral wall portion 71b.
  • the connecting peripheral wall portion 71b may be formed by the case bottom wall 25b of the case 25 or a wall portion extending from the front surface 311 of the first end plate 31 toward the inside of the discharge chamber 16 in the direction of the drive axis O1. The same applies to the compressors of Examples 2 and 3.
  • the collision cylinder 81 may be arranged inside the case 25 in a state where the front-to-back direction is reversed compared to Example 2, and the collision cylinder 81 may be fixed to the case bottom wall 25b of the case 25 by the first fixing bolt 50a.
  • the case bottom wall 26b has protrusions 266-269.
  • the collision wall 91 may have protrusions 266-269, and the protrusions 266-269 may protrude from the second surface 912 of the collision wall 91 toward the case bottom wall 26b.
  • first to fourth radial flow passages 15a to 15d are formed between the second surface 912 of the collision wall 91 and the rear surface 265b of the main body 265.
  • this is not limited to this, and only the first radial flow passage 15a may be formed between the second surface 912 of the collision wall 91 and the rear surface 265b of the main body 265, or a radial flow passage may be formed in addition to the first to fourth radial flow passages 15a to 15d.
  • downstream passage portion 153 may be connected to the upstream passage portion 152 in a straight line without being curved. The same applies to the compressor of Example 5.
  • the downstream passage section 153 may be omitted, and the first to fourth radial flow paths 15a to 15d may be formed by the inlet section 151 and the upstream passage section 152.
  • the upstream passage portion 152 may extend from the inlet portion 151 side toward the discharge passage 26d side while inclining in the same direction as the rotation direction R1 of the first scroll 30. The same applies to the compressor of Example 5.
  • a compressor may be constructed by combining the compressor of Example 2 with the compressor of Example 4, or a compressor may be constructed by combining the compressor of Example 3 with the compressor of Example 4.
  • This specification also includes the following inventions.
  • Appendix 1 a housing, a drive mechanism, a first scroll, and a second scroll; the drive mechanism, the first scroll, and the second scroll are housed in the housing;
  • a scroll compressor in which a compression chamber for compressing a refrigerant is formed by the first scroll and the second scroll,
  • the housing is formed with a discharge port for discharging the compressed refrigerant, which is the refrigerant compressed in the compression chamber, to the outside.
  • a case is fixed to at least one of the first scroll, the second scroll, and the drive mechanism so as to be rotatable within the housing;
  • the case includes a discharge chamber that communicates with the compression chamber and into which the compressed refrigerant is discharged from the compression chamber.
  • a discharge passage communicating with the discharge chamber and the discharge communication port is formed; a collision wall that rotates together with the case and collides with the compressed refrigerant flowing toward the discharge passage, thereby separating lubricating oil contained in the compressed refrigerant from the compressed refrigerant, within the discharge chamber; (Appendix 2) the first scroll is driven to rotate about a drive axis by the drive mechanism, the second scroll is eccentric with respect to the first scroll and is rotated around a driven axis by the first scroll and a driven mechanism, the case is fixed to the first scroll, 2.
  • the first scroll has a discharge port formed therein that communicates with the compression chamber.
  • the collision wall has a plate shape extending in a radial direction of the first scroll, and includes an opposing wall portion facing the first scroll while being spaced apart from the first scroll in the drive shaft direction, and a connecting peripheral wall portion connected to the opposing wall portion and extending cylindrically in the drive shaft direction,
  • the discharge chamber is divided into a first discharge chamber and a second discharge chamber by the collision wall, the first discharge chamber is located between the collision wall and the first scroll and communicates with the discharge port; the second discharge chamber is located between the case and the collision wall and communicates with the discharge passage; 3.
  • the connecting peripheral wall portion has a communication passage extending in the radial direction and communicating between the first discharge chamber and the second discharge chamber.
  • the collision wall has a plate shape extending in a radial direction of the first scroll, and includes an opposing wall portion facing the first scroll while being spaced apart from the first scroll in the drive shaft direction, and a connecting peripheral wall portion connected to the opposing wall portion and extending cylindrically in the drive shaft direction,
  • the discharge chamber is divided into a first discharge chamber and a second discharge chamber by the collision wall, the first discharge chamber is located between the collision wall and the first scroll and communicates with the discharge port; the second discharge chamber is located between the case and the collision wall and communicates with the discharge passage; 3.
  • a communication passage extending in the drive shaft direction and communicating between the first discharge chamber and the second discharge chamber is formed in the opposing wall portion.
  • the first scroll is provided with a discharge valve disposed in the discharge chamber and capable of opening and closing the discharge port; 5.
  • the collision wall has a first surface facing the discharge valve in the drive shaft direction, and a second surface located on the opposite side of the first surface and abutting against the case in the drive shaft direction, the discharge passage is covered by the collision wall while facing the second surface in the drive shaft direction, 6.
  • the radial flow path has an inlet portion that opens into the discharge chamber; an upstream flow path portion connected to the inlet portion and allowing the compressed refrigerant to flow from the inlet portion toward the discharge passage, 7.
  • the radial flow path has a downstream flow path portion that communicates with the discharge passage, 8.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Ce compresseur à spirales comprend un logement (6), un mécanisme d'entraînement (10), une première spirale (30) et une seconde spirale (40). La première spirale (30) et la seconde spirale (40) forment une chambre de compression (12) pour comprimer un fluide frigorigène. Un boîtier (25) est fixé à la première spirale (30). Une chambre d'évacuation (16), un trajet de recirculation (250) et un passage d'évacuation (251) sont formés dans le boîtier (25). La chambre d'évacuation (16) communique avec la chambre de compression (12), et un fluide frigorigène comprimé, qui est un fluide frigorigène comprimé par la chambre de compression (12), est évacué. Une paroi de collision (71) est disposée dans la chambre d'évacuation (16), et la paroi de collision (71) tourne conjointement avec le boîtier (25). La paroi de collision (71) sépare une huile lubrifiante (18) contenue dans le fluide frigorigène comprimé du fluide frigorigène comprimé en entrant en collision avec le fluide frigorigène comprimé s'écoulant vers le passage d'évacuation (251).
PCT/JP2025/002630 2024-03-26 2025-01-28 Compresseur à spirale Pending WO2025204084A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2024-049973 2024-03-26
JP2024049973 2024-03-26
JP2024-133803 2024-08-09
JP2024133803A JP2025149788A (ja) 2024-03-26 2024-08-09 スクロール型圧縮機

Publications (1)

Publication Number Publication Date
WO2025204084A1 true WO2025204084A1 (fr) 2025-10-02

Family

ID=97218596

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2025/002630 Pending WO2025204084A1 (fr) 2024-03-26 2025-01-28 Compresseur à spirale

Country Status (1)

Country Link
WO (1) WO2025204084A1 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02227579A (ja) * 1989-02-28 1990-09-10 Toshiba Corp スクロール流体機械
US20180223843A1 (en) * 2017-02-06 2018-08-09 Emerson Climate Technologies, Inc. Co-rotating compressor

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02227579A (ja) * 1989-02-28 1990-09-10 Toshiba Corp スクロール流体機械
US20180223843A1 (en) * 2017-02-06 2018-08-09 Emerson Climate Technologies, Inc. Co-rotating compressor

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