WO2017056837A1 - Compresseur à vis - Google Patents

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Publication number
WO2017056837A1
WO2017056837A1 PCT/JP2016/075512 JP2016075512W WO2017056837A1 WO 2017056837 A1 WO2017056837 A1 WO 2017056837A1 JP 2016075512 W JP2016075512 W JP 2016075512W WO 2017056837 A1 WO2017056837 A1 WO 2017056837A1
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WO
WIPO (PCT)
Prior art keywords
motor
oil
rotor
shaft
lubricating oil
Prior art date
Application number
PCT/JP2016/075512
Other languages
English (en)
Japanese (ja)
Inventor
昇 壷井
元 中村
克徳 濱田
Original Assignee
株式会社神戸製鋼所
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
Application filed by 株式会社神戸製鋼所 filed Critical 株式会社神戸製鋼所
Priority to CN201680056959.4A priority Critical patent/CN108138781B/zh
Publication of WO2017056837A1 publication Critical patent/WO2017056837A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation

Definitions

  • the present invention relates to a screw compressor, and more particularly, to a screw compressor having a cooling structure for cooling a motor that rotationally drives a screw rotor.
  • a pair of male and female screw rotors are driven to rotate by a motor.
  • the motor When the motor is driven to rotate at high speed, the motor generates heat due to electrical loss such as so-called iron loss (hysteresis loss and eddy current loss) and copper loss (loss due to winding resistance). Therefore, a cooling jacket for cooling the generated motor is provided on the outer periphery of the motor casing, and the motor is cooled by exchanging heat with a liquid medium such as cooling water or coolant flowing through the cooling jacket (patent). Reference 1).
  • a technical problem to be solved by the present invention is to provide a screw compressor having a cooling structure that cools a motor that rotationally drives the screw rotor from the inside.
  • the present invention provides the following screw compressor.
  • a compressor body in which a pair of male and female screw rotors arranged in the horizontal direction and meshing with each other is housed in the rotor chamber of the rotor casing;
  • a motor in which a rotor and a stator are housed in a motor chamber of a motor casing, and a rotor shaft of the screw rotor is driven to rotate by a motor shaft fixed to the rotor;
  • An oil supply passage for supplying lubricating oil to the oil supply destination;
  • An intermediate bearing portion provided on the motor side for supporting the rotor shaft and lubricated by the flow of lubricating oil;
  • An oil discharger for discharging the lubricating oil introduced into the motor chamber through the oil supply path to the outside of the motor chamber;
  • an oil recovery part for recovering the lubricating oil discharged from the oil drain part.
  • the lubricating oil supplied to the intermediate bearing portion and guided into the motor chamber is transmitted through the motor shaft, thereby cooling the motor shaft.
  • Lubricating oil transmitted through the motor shaft is converted into oil mist by a rotor that rotates in the motor chamber, adheres to the rotor, the stator, and the motor shaft in the motor chamber, and cools the motor.
  • Lubricating oil used for cooling is collected in the oil collecting section, and cooling of the motor is not hindered. Therefore, the motor that rotationally drives the screw rotor can be effectively cooled by the lubricating oil supplied to the intermediate bearing portion.
  • the cross-sectional view of the screw compressor which concerns on 1st Embodiment of this invention The longitudinal cross-sectional view of the screw compressor shown in FIG.
  • the fragmentary sectional view of the motor chamber in the screw compressor shown in FIG. The expanded sectional view of the motor side bearing part periphery in the screw compressor shown in FIG.
  • the expanded sectional view of the intermediate bearing part periphery in the screw compressor shown in FIG. FIG. 6 is a cross-sectional view taken along line VI-VI in FIG. 5.
  • the fragmentary sectional view of the motor room in the screw compressor concerning a 2nd embodiment of this invention.
  • the longitudinal cross-sectional view of the screw compressor which concerns on 3rd Embodiment of this invention.
  • FIG. 1 is a cross-sectional view of a screw compressor 1 according to the first embodiment.
  • This screw compressor 1 is an oil-free screw compressor.
  • a pair of screw rotors 3 including a male rotor 3 a and a female rotor 3 b that mesh with each other in an oil-free state are accommodated in a rotor chamber 17 formed in the rotor casing 4 of the oil-free compressor body 2.
  • a bearing casing 7 is attached to the suction side end of the rotor casing 4.
  • a motor casing 5 of the motor 6 is attached to the discharge side end of the rotor casing 4.
  • the motor 6 includes a rotor 6a, a stator 6b, and a motor casing 5.
  • the motor casing 5 includes a motor casing body 5a, a cooling jacket 8, and a cover 9.
  • a rotor (rotor) 6a and a stator (stator) 6b are accommodated in the motor casing body 5a.
  • the end of the motor casing 5 is closed with a cover 9.
  • a gas discharge port (not shown) is formed on the motor 6 side of the rotor casing 4, and a gas suction port (not shown) is formed on the rotor casing 4 on the opposite side of the motor 6.
  • Timing gears (not shown) that mesh with each other are attached to shaft ends of the male rotor 3a and the female rotor 3b opposite to the motor 6. Normally, the male rotor 3 a is driven to rotate by the motor 6. The rotation of the motor shaft 31 of the motor 6 causes the male rotor shaft 21 of the male rotor 3a to rotate, and the female rotor shaft 22 of the female rotor 3b rotates so as to synchronize with the male rotor shaft 21 via the timing gear. .
  • the motor 6 is a drive source for rotating the rotor shaft (usually the male rotor shaft 21) of the screw rotor 3.
  • the rotation speed of the motor 6 is controlled by an inverter (not shown), and the motor 6 is operated at a high speed rotation exceeding 20000 rpm, for example.
  • the rotor 6a of the motor 6 is fixed to the outer peripheral portion of the motor shaft 31, and the stator 6b is arranged apart from the rotor 6a.
  • An air gap 6g is formed between the rotor 6a and the stator 6b.
  • the cooling jacket 8 is disposed between the stator 6b and the motor casing body 5a so as to be in close contact with the stator 6b.
  • the motor shaft 31 has a plurality of different-diameter shaft portions that reduce the diameter from the screw rotor 3 side toward the motor-side bearing portion 13 side. As shown in FIG. 3, the motor shaft 31 includes, for example, a first shaft portion 44 and a second shaft portion 45. The large-diameter first shaft portion 44 is locked to the side end surface of the rotor 6a. The rotor 6a is attached to the second shaft portion 45 having a small diameter.
  • the connection hole 32 extends in the axial direction over the entire first shaft portion 44 and a part of the second shaft portion 45.
  • the center hole 33 extends in the axial direction over the remaining portion of the second shaft portion 45.
  • the rotor 6 a is fixed to the motor shaft 31 by tightening with the mounting bolts 38 in a state where the flange portion of the bearing support 37 is in contact with each of the second shaft portion 45 and the side end surface of the rotor 6 a.
  • the cooling jacket 8 is fixed along the inner surface of the motor casing main body 5a and fastened with bolts in a state where the flange portions are in contact with each other, whereby the cooling jacket 8 is fixed to the motor casing main body 5a.
  • a cooling passage 8b is formed for flowing cooling water or cooled lubricating oil. Liquid leakage from the cooling passage 8b into the motor casing body 5a is prevented by packing provided on both sides in the axial direction of the cooling passage 8b.
  • the male rotor shaft 21 of the screw rotor 3 and the motor shaft 31 of the motor 6 are configured separately, and a key to be described later is provided so that both the shafts 21 and 31 extend coaxially in the horizontal direction (lateral direction). 41 (coupling member) is integrally connected.
  • the opposite side of the motor 6 in the male rotor shaft 21 is supported on the bearing casing 7 by the rotor-side bearing portion 11.
  • the motor 6 side of the male rotor shaft 21 is supported on the rotor casing 4 by the intermediate bearing portion 12. That is, the male rotor shaft 21 is supported by the rotor-side bearing portion 11 and the intermediate bearing portion 12 in both ends.
  • the bearing support 37 fixed to the motor side end of the motor shaft 31 is supported by the cover 9 by the motor side bearing 13.
  • the integrally connected male rotor shaft 21 and motor shaft 31 extend coaxially in the horizontal direction (laterally), and at three locations of the rotor-side bearing portion 11, the intermediate bearing portion 12, and the motor-side bearing portion 13. Supported (that is, supported at three points).
  • the female rotor shaft 22 of the female rotor 3 b is supported on the bearing casing 7 and the rotor casing 4 by both ends by a rotor side bearing portion 15 and an intermediate bearing portion 16 that are located on the opposite side of the motor 6.
  • the rotor-side bearing portion 11 that supports the male rotor shaft 21 includes, for example, a thrust bearing (4-point contact ball bearing) 11a and a radial bearing (roller bearing) 11b.
  • the intermediate bearing portion 12 includes, for example, a radial bearing (roller bearing) 12a provided on the screw rotor 3 side and a thrust bearing (four-point contact ball bearing) 12b provided on the motor side.
  • an intermediate oil supply passage 82 for supplying lubricating oil to the intermediate bearing portion 12 is provided between the radial bearing 12a and the thrust bearing 12b.
  • the motor side bearing portion 13 is constituted by, for example, a radial bearing (deep groove ball bearing).
  • the rotor side bearing portion 15 that supports the female rotor shaft 22 includes, for example, a thrust bearing (four-point contact ball bearing) 15a and a radial bearing (roller bearing) 15b.
  • the intermediate bearing portion 16 includes, for example, a radial bearing (roller bearing) 16a and a thrust bearing (four-point contact ball bearing) 16b.
  • a bearing (corresponding to the thrust bearing 12b in the present embodiment) that supports at least the rotor shaft (here, the male rotor shaft 21) connected to the motor shaft 31 on the motor 6 side is lubricated to the motor 6 side.
  • An open-type bearing is used so that it can be lubricated.
  • the other bearings also use the open type, but for each of the other bearings, whether or not to make an open type bearing is considered in consideration of the load on the bearing and the manner of lubrication. What is necessary is just to determine suitably.
  • An intermediate shaft sealing portion 14 a is provided on the male rotor shaft 21 between the male rotor 3 a and the intermediate bearing portion 12.
  • a shaft seal portion 14c is provided on the male rotor shaft 21 between the rotor-side bearing portion 11 and the male rotor 3a.
  • a shaft sealing portion 14 b is provided on the female rotor shaft 22 between the female rotor 3 b and the intermediate bearing portion 16.
  • a shaft sealing portion 14d is provided on the female rotor shaft 22 between the rotor-side bearing portion 15 and the female rotor 3b.
  • Each shaft seal part 14a, 14b, 14c, 14d is provided with the mechanical seal as a visco seal and an air seal, for example as an oil seal.
  • the visco seal provided on the bearing side prevents the lubricating oil from flowing into the rotor chamber 17.
  • the mechanical seal provided on the screw rotor 3 side prevents inflow of lubricating oil into the rotor chamber 17 and excessive leakage of compressed gas from the rotor chamber 17.
  • the protruding end portion of the bearing support 37 is inserted into the center hole 33 of the motor shaft 31 and is tightened with the mounting bolt 38 in a state where the flange portion of the bearing support 37 is in contact with the side end surface of the motor shaft 31. .
  • the bearing support 37 is fixed to the motor shaft 31 and one end of the center hole 33 on the motor side bearing portion 13 side is closed.
  • the inner ring of the motor side bearing portion 13 is positioned so as not to move in the axial direction by a stop ring 61 disposed on the bearing support 37.
  • the motor-side bearing portion 13 is attached to the bearing mounting hole 9a of the cover 9 with a clearance fit.
  • wheel of the motor side bearing part 13 can move to an axial direction. That is, the motor side bearing portion 13 is assembled to the motor 6 so as to allow sliding in the axial direction on the outer ring. According to the said structure, even if the motor shaft 31 expand
  • the cover 9 is attached to the cooling jacket 8 so as to close the opening of the motor casing 5.
  • the cover 9 is fixed to the cooling jacket 8 by tightening with a bolt while the flange portion of the cover 9 is in contact with the side end surface of the cooling jacket 8.
  • the shaft diameter of the motor shaft 31 of the motor 6 is larger than the shaft diameter of the male rotor shaft 21 of the screw rotor 3.
  • a connecting hole 32 for inserting the connecting end 24 on the motor 6 side of the male rotor shaft 21 is formed in the motor shaft 31 having a large diameter.
  • the motor shaft 31 is formed with a center hole 33 having a diameter larger than that of the connection hole 32.
  • the fastening flange 27 can be freely inserted through the center hole 33 due to the level difference of the through-hole penetrating the motor shaft 31, but it is a dead end with respect to the connection hole 32.
  • the fastening flange 27 has a screw insertion hole and a plurality of flange communication holes 27a.
  • the plurality of flange communication holes 27a communicate the center hole 33 and the oil guide hole 21c.
  • a concave second key groove 31a having a rectangular cross section is formed on the inner peripheral surface 31b of the connecting hole 32 provided in the motor shaft 31, for example.
  • a concave first key groove 24a having a rectangular cross section is formed on the outer peripheral surface 21b of the connecting end portion 24 provided on the male rotor shaft 21, for example.
  • a rectangular key groove 42 is formed in the axial direction by the first key groove 24a and the second key groove 31a.
  • a fastening portion 25 is provided inside the connecting end portion 24.
  • the fastening portion 25 includes an oil guide hole 21 c and a screw hole 26 that extend in the axial direction from the end surface of the connecting end portion 24.
  • the hole diameter of the oil guide hole 21 c is larger than that of the screw hole 26.
  • a space is formed between the connecting end portion 24 and the fastening flange 27 to form a flow path connecting the oil guide hole 21c and the flange communication hole 27a. Therefore, the lubricating oil that has passed through the flange communication hole 27 a can flow through the annular gap formed between the oil guide hole 21 c and the fastening bolt 28.
  • a plurality of oil outlet holes 21d extending in the direction perpendicular to the axis are formed.
  • the plurality of oil outlet holes 21 d communicate with the oil guide hole 21 c and the motor chamber 20.
  • a part of the motor shaft communication portion 39 is configured by the communication between the center hole 33, the plurality of flange communication holes 27 a, the oil guide hole 21 c, and the plurality of oil lead-out holes 21 d.
  • the screw part 28 b of the fastening bolt 28 is screwed into the screw hole 26 of the fastening part 25.
  • a fastening bolt 28 as a fastening member is inserted through the screw insertion hole of the fastening flange 27.
  • the fastening bolt 28 is tightened in a state where the fastening flange 27 is inserted into the center hole 33 and engaged with the step of the through hole, the connecting end portion 24 of the male rotor shaft 21 is drawn toward the motor side bearing portion 13.
  • the head 28 a of the fastening bolt 28 is engaged with the fastening flange 27.
  • the motor shaft 31 and the male rotor shaft 21 are fastened by the fastening bolt 28.
  • the motor shaft 31 and the male rotor shaft 21 are fastened by the fastening bolts 28 in a state where the motor shaft 31 and the male rotor shaft 21 are integrally connected by the key 41.
  • the motor shaft 31 and the male rotor shaft 21 are integrally connected by a key 41 as a coupling member, and the motor shaft 31 and the male rotor shaft 21 fastened by a fastening bolt 28 as a fastening member are a single shaft body. Work as. Since the fitting structure using the key 41 is not affected by the lubricating oil, even if the lubricating oil enters the connecting hole 32 through the male rotor shaft 21 extending in the horizontal direction, the motor shaft Torque can be reliably transmitted between 31 and the male rotor shaft 21.
  • the head portion 28a of the fastening bolt 28 is located in the center hole 33 formed so as to penetrate the motor shaft 31 in the axial direction. Specifically, the head portion 28 a is immersed in the center hole 33 of the motor shaft 31 so that the head portion 28 a is positioned in the vicinity of the shaft end surface of the fastening portion 25 of the male rotor shaft 21. That is, the axial length of the fastening bolt 28 is configured to be short. According to the said structure, the influence of the thermal expansion of the fastening bolt 28 decreases, and it can clamp
  • the connection end 24 and the fastening portion 25 of the male rotor shaft 21 and the connection hole 32 and the center hole 33 of the motor shaft 31 extend coaxially.
  • the radial bearing 12a of the intermediate bearing portion 12 is attached to the rotor casing 4 on the motor 6 side.
  • the position of the inner ring of the radial bearing 12a is fixed with respect to the male rotor shaft 21, and the position of the outer ring of the radial bearing 12a is fixed with respect to the rotor casing 4 by a retaining ring.
  • a bearing support member 19 is attached to the rotor 6 on the motor 6 side via the spacer 18. By tightening with bolts, the bearing support member 19 and the spacer 18 are fixed to the motor 6 side of the rotor casing 4.
  • the position of the inner ring of the thrust bearing 12b is fixed to the male rotor shaft 21 by a locking nut 23a.
  • a radial bearing 16 a of the intermediate bearing portion 16 is attached to the motor 6 side of the rotor casing 4.
  • the position of the inner ring of the radial bearing 16a is fixed with respect to the female rotor shaft 22, and the position of the outer ring of the radial bearing 16a is fixed with respect to the rotor casing 4 by a retaining ring.
  • the position of the inner ring of the thrust bearing 16b is fixed to the female rotor shaft 22 by a locking nut 23b.
  • the inner ring, outer ring, and rolling elements constituting the bearing are usually made of steel and have conductivity. Therefore, the high frequency current from the inverter circuit of the motor 6 flows to the intermediate bearing portion 12 and the motor side bearing portion 13 that support the motor shaft 31 of the motor 6, and the outer ring and the inner ring of the intermediate bearing portion 12 and the motor side bearing portion 13. A shaft voltage is generated in the meantime, which causes an electrolytic corrosion phenomenon that damages the bearing. Therefore, the intermediate bearing portion 12 and the motor side bearing portion 13 are electrically insulated.
  • the bearing is electrically insulated because, for example, the rolling element of the bearing is made of an inorganic insulating material such as ceramics, and the outer surface of at least one of the inner ring and outer ring of the bearing is epoxy resin, unsaturated polyester resin, etc. It is covered with an organic insulating material. Moreover, in the support member and casing which support a bearing, the part contact
  • an intermediate oil supply port 64 communicating with the intermediate oil supply passage 82 is formed in the upper portion of the rotor casing 4.
  • An intermediate oil supply hole 82 a extending from the intermediate oil supply port 64 to the intermediate bearing portion 12 is formed in the rotor casing 4.
  • a radial bearing 12 a and a thrust bearing 12 b are arranged apart from each other by a spacer 18.
  • a communication space 82b is formed between the separated radial bearing 12a and thrust bearing 12b.
  • the intermediate oil supply hole 82a communicates with the communication space 82b. Therefore, the intermediate oil supply passage 82 communicates with the communication space 82 b through the intermediate oil supply hole 82 a in the rotor casing 4.
  • the lubricating oil supplied to the intermediate oil supply passage 82 is supplied to each of the radial bearing 12a and the thrust bearing 12b of the intermediate bearing portion 12 through the communication space 82b.
  • the lubricating oil supplied to the radial bearing 12a is used for lubrication and cooling of the radial bearing 12a.
  • the lubricating oil is restricted from flowing toward the rotor chamber 17 by the oil seal of the intermediate shaft sealing portion 14a.
  • the rotor casing 4 includes an intermediate communication portion 54 having one end communicating with a gap formed between the radial bearing 12 a and the intermediate shaft sealing portion 14 a and the other end communicating with the motor chamber 20.
  • the lubricating oil that is about to flow from the radial bearing 12 a to the screw rotor 3 side is guided into the motor chamber 20 through the intermediate communication portion 54.
  • the lubricating oil introduced into the motor chamber 20 through the intermediate communication portion 54 is discharged from the oil discharge portion to the outside of the motor chamber 20 and is recovered by the oil recovery portion 71.
  • the intermediate communication portion 54 it is possible to prevent the lubricating oil from flowing into the rotor chamber 17 beyond the intermediate shaft sealing portion 14a even when the open type is used for the radial bearing 12a.
  • the low-pressure stage screw rotor 3 includes the intermediate communication portion 54 when the discharge side of the low-pressure stage has a negative pressure.
  • the inflow of lubricating oil into the rotor chamber 17 can be effectively prevented.
  • the lubricating oil supplied to the thrust bearing 12b is used for lubrication and cooling of the thrust bearing 12b.
  • the lubricating oil that has been lubricated and cooled while flowing through the thrust bearing 12b is guided into the motor chamber 20 to cool the motor shaft 31 from the outer surface.
  • the lubricating oil is finely divided into oil mist by the motor shaft 31 and the rotor 6a that rotate at high speed in the motor chamber 20.
  • the lubricating oil that has become oil mist adheres to the rotor 6 a, the stator 6 b, and the motor shaft 31 in the motor chamber 20, and cools the motor 6 from the motor chamber 20.
  • a rotor-side motor chamber oil supply port 65 communicating with the rotor-side motor chamber oil supply passage 83 is formed in the upper portion of the motor chamber 20 on the intermediate bearing portion 12 side, that is, in the upper portion of the motor casing 5 on the intermediate bearing portion 12 side. Yes.
  • the motor chamber oil supply passage 83 on the rotor side and the motor chamber oil supply port 65 on the rotor side function as a motor chamber oil supply passage and a motor chamber oil supply port, respectively.
  • the motor chamber oil supply port 65 on the rotor side is provided with a nozzle (not shown) that can inject lubricating oil into fine particles.
  • the lubricating oil supplied to the motor chamber oil supply passage 83 on the rotor side is guided into the motor chamber 20 through the nozzle.
  • the lubricating oil introduced into the motor chamber 20 adheres to the rotor 6a, the stator 6b, and the motor shaft 31 in the motor chamber 20 to cool the motor 6.
  • An intermediate oil discharge port 66 communicating with the intermediate oil discharge passage 92 is formed at the bottom of the motor chamber 20 on the intermediate bearing portion 12 side, that is, at the bottom of the motor casing 5 on the intermediate bearing portion 12 side.
  • the intermediate oil discharge passage 92 and the intermediate oil discharge port 66 function as a motor chamber oil discharge passage and a motor chamber oil discharge port (oil discharge portion), respectively.
  • Lubricating oil used for lubricating the intermediate bearing portion 12 and cooling the motor 6 gathers at the bottom of the motor chamber 20 on the intermediate bearing portion 12 side and is discharged out of the motor chamber 20 through the intermediate oil discharge port 66.
  • the lubricating oil is recovered by the oil recovery unit 71 through the intermediate oil discharge passage 92.
  • the motor casing 5 that forms a cooling jacket 8 on the motor side bearing portion 13 is formed at the motor side oil supply port 77 on the motor side communicating with the motor chamber oil supply passage 86 on the motor side. It is formed on the top of.
  • the motor chamber oil supply passage 86 on the motor side and the motor chamber oil supply port 77 on the motor side function as a motor chamber oil supply passage and a motor chamber oil supply port, respectively.
  • the motor chamber oil supply port 77 on the motor side is opened so that the lubricating oil flows out toward the winding of the stator 6b.
  • a motor-side bearing oil supply hole 79 is formed in the upper part of the cover 9 located below the winding of the stator 6b.
  • the motor-side bearing oil supply hole 79 has an oil receiving portion having a concave opening at the top.
  • the lubricating oil supplied to the motor chamber oil supply passage 86 on the motor side is supplied into the motor chamber 20 through the motor chamber oil supply port 77 on the motor side, and cools the windings of the stator 6b.
  • Lubricating oil that has flowed below the windings of the stator 6 b is collected in the oil receiving portion and supplied to the motor-side bearing portion 13 through the motor-side bearing oil supply hole 79.
  • the lubricating oil supplied to the motor side bearing portion 13 is used for lubrication and cooling of the motor side bearing portion 13.
  • the lubricating oil that has lubricated and cooled the motor-side bearing 13 is guided into the motor chamber 20.
  • a motor chamber oil drain port 78 that communicates with the motor chamber oil drain passage 93 on the motor side forms a cooling jacket 8 on the motor side bearing portion 13 side, that is, on the motor side bearing portion 13 side. It is formed at the bottom of the casing 5.
  • the motor side oil discharge passage 93 on the motor side and the motor chamber oil discharge port 78 on the motor side function as a motor chamber oil discharge passage and a motor chamber oil discharge port (oil discharge portion), respectively.
  • Lubricating oil used for lubricating the motor-side bearing portion 13 and cooling the windings of the stator 6b of the motor 6 gathers at the bottom of the motor chamber 20 on the motor-side bearing portion 13 side, and the motor-side oil discharge port on the motor side. It is discharged outside the motor chamber 20 through 78.
  • the lubricating oil is recovered by the oil recovery portion 71 through the motor chamber oil drain passage 93 on the motor side.
  • a rotor side bearing oil supply port (not shown) communicating with the rotor side bearing oil supply passage 81 is formed in the upper part of the bearing casing 7 on the rotor side bearing portion 11 side.
  • a rotor side bearing oil supply hole (not shown) extending from the rotor side bearing oil supply port to the rotor side bearing portion 11 is formed in the bearing casing 7.
  • the lubricating oil supplied to the rotor side bearing oil supply passage 81 is supplied to the rotor side bearing portion 11 through the rotor side bearing oil supply hole.
  • the lubricating oil supplied to the rotor side bearing portion 11 is used for lubrication and cooling of the rotor side bearing portion 11.
  • the lubricating oil that has lubricated and cooled the rotor-side bearing portion 11 is restricted from flowing toward the rotor chamber 17 by the oil seal of the shaft seal portion 14c.
  • a rotor-side bearing oil discharge port (not shown) that leads from the rotor-side bearing portion 11 to the rotor-side bearing oil drain passage 91 is formed.
  • the lubricating oil used for the lubrication and cooling of the rotor side bearing portion 11 is discharged out of the bearing casing 7 through the rotor side bearing oil discharge port.
  • the lubricating oil is recovered by the oil recovery portion 71 through the rotor side bearing oil drain passage 91.
  • a jacket oil supply port 67 communicating with the jacket oil supply passage 84 is formed in the upper part of the motor casing 5.
  • the jacket oil supply port 67 communicates with the cooling passage 8b.
  • the lubricating oil supplied to the jacket oil supply path 84 is supplied to the cooling passage 8b through the jacket oil supply port 67 to cool the stator 6b.
  • a jacket oil discharge port 68 communicating with the jacket oil discharge passage 94 is formed in the lower part of the motor casing 5.
  • a downstream side of the cooling jacket 8 communicates with a jacket oil discharge path 94 that constitutes a part of the oil discharge path 90.
  • the jacket oil discharge port 68 communicates with the cooling passage 8b.
  • the lubricating oil that has flowed through the cooling passage 8 b is discharged out of the motor casing 5 through the jacket oil outlet 68.
  • the lubricating oil is recovered by the oil recovery unit 71 through the jacket oil discharge passage 94. Therefore, the lubricating oil that lubricates and cools the bearing portions 11, 12, and 13 can be used to cool the stator 6 b of the motor 6 by flowing through the cooling passage 8 b of the cooling jacket portion 8 a.
  • the motor shaft oil supply member 10 includes an attachment flange 10 a and a protrusion 10 b and is attached in a sealed state to the opening on the side surface of the cover 9.
  • a motor shaft oil supply port 69 is formed at the center of the mounting flange 10a.
  • An oil introduction hole 10c is formed inside the protruding portion 10b extending in the axial direction.
  • the oil introduction hole 10 c is a through hole extending in the axial direction, and communicates the motor shaft oil supply port 69 and the insertion hole 37 c of the bearing support 37.
  • An insertion hole 37 c is formed at the center of the bearing support 37.
  • the insertion hole 37c is a through-hole that is larger in diameter than the protruding portion 10b of the motor shaft oil supply member 10 and extends in the axial direction so that the protruding portion 10b can be inserted through a slight gap.
  • the oil introduction hole 10 c and the insertion hole 37 c are arranged coaxially with respect to the center hole 33.
  • a part of the protrusion 10b is inserted into the insertion hole 37c so that the end of the protrusion 10b overlaps the insertion hole 37c in the axial direction.
  • a part of the motor shaft communication portion 39 is configured by the communication of the oil introduction hole 10 c, the insertion hole 37 c, and the center hole 33.
  • the motor shaft communication portion 39 is configured by the communication of the oil introduction hole 10c, the insertion hole 37c, the center hole 33, the plurality of flange communication holes 27a, the oil guide holes 21c, and the plurality of oil outlet holes 21d.
  • the lubricating oil supplied from the motor shaft oil supply port 69 communicating with the motor shaft oil supply passage 85 flows through the center hole 33 formed in the motor shaft 31, and passes through the rotor 6 a from the inside (inside). Cooling. The lubricating oil that has flowed through the center hole 33 cools the motor shaft 31 from the inside (inside).
  • the center hole 33 extending in the axial direction along the rotor 6a has a diameter larger than that of the insertion hole 37c (in the present embodiment, the diameter is increased by three times or more in diameter). Thereby, the surface area (heat transfer surface) of the center hole 33 can be increased, and the cooling effect of the rotor 6a can be enhanced.
  • Lubricating oil that has flowed out from the plurality of oil outlet holes 21d is finely divided into oil mist by the motor shaft 31 and the rotor 6a that rotate at a high speed in the motor chamber 20.
  • the lubricating oil that has become oil mist adheres to the rotor 6a, the stator 6b, and the motor shaft 31 in the motor chamber 20 to cool the motor 6.
  • the lubricating oil used for cooling the motor 6 is discharged out of the motor chamber 20 through the intermediate oil discharge port 66.
  • the lubricating oil is recovered by the oil recovery unit 71 through the intermediate oil discharge passage 92.
  • the oil drain passage 90 is connected to an oil recovery portion 71 that recovers the lubricating oil.
  • An oil cooler 72 that cools the recovered lubricating oil is provided on the downstream side of the oil recovery unit 71.
  • An oil supply passage 80 for supplying lubricating oil to the oil supply destination is connected to the downstream side of the oil pump 73.
  • the oil supply destination is the rotor side bearing portion 11, the intermediate bearing portions 12 and 16, the motor side bearing portion 13 and the like.
  • the lubricating oil is also supplied to the inside of the motor chamber 20, the cooling jacket 8, and the center hole 33 of the motor shaft 31 as a cooling medium. Therefore, the oil supply passage 80 branches into a rotor-side bearing oil supply passage 81, an intermediate oil supply passage 82, a rotor-side motor chamber oil supply passage 83, a jacket oil supply passage 84, a motor shaft oil supply passage 85, and a motor-side motor chamber oil supply passage 86. Yes.
  • Each of the oil supply passages 81, 82, 83, 84, 85, and 86 includes a rotor side bearing oil supply port, an intermediate oil supply port 64, a rotor side motor chamber oil supply port 65, a jacket oil supply port 67, a motor shaft oil supply port 69, and a motor on the motor side. It leads to each of the chamber refueling ports 77. Accordingly, the lubricating oil is supplied to each oil supply destination that requires lubrication and cooling in the compressor body 2 and the motor 6 and is used for lubrication and cooling at each oil supply destination. And the process of being cooled by the oil cooler 72 is repeated. Thus, the lubricating oil is circulated and used in the screw compressor 1.
  • the motor casing 5 is attached to the discharge side of the rotor casing 4, and the motor shaft 31 of the motor 6 extends to the discharge side of the rotor casing 4.
  • the discharge side of the rotor casing 4 becomes hot due to gas compression by the screw rotor 3, and the motor shaft 31 also becomes hot. Cooling the motor shaft 31 at a high temperature with the lubricating oil makes the cooling effect of the lubricating oil more remarkable.
  • the shaft diameter of the motor shaft 31 is configured to be larger than the shaft diameter of the male rotor shaft 21.
  • the motor shaft 31 is coupled to the male rotor shaft 21 by inserting the coupling end 24 of the male rotor shaft 21 into the coupling hole 32 formed in the motor shaft 31.
  • the motor shaft 31 serves as one shaft and the male rotor shaft 21 serves as the other shaft.
  • the shaft diameter of the male rotor shaft 21 is larger than the shaft diameter of the motor shaft 31, the male rotor shaft 21 functions as one shaft, Can be configured to work as an axis.
  • a second key groove 31a having a rectangular cross section and a concave shape is formed on the outer peripheral surface 34b of the connecting end 34 provided on the motor shaft 31, for example.
  • a concave first key groove 24a having a rectangular cross section is formed on the inner peripheral surface 24b of the connecting hole 23 provided in the male rotor shaft 21, for example.
  • the first key groove 24a and the second key groove 31a constitute a key groove 42 having a rectangular cross section.
  • the key 41 having a rectangular cross section connects the outer peripheral surface 34 b of the connecting end 34 of the motor shaft 31 and the male rotor shaft 21. It is interposed between the inner peripheral surface 24 b of the hole 23.
  • the key 41 is fitted in the key groove 42 by fitting the key 41 in the key groove 42. Therefore, the motor shaft 31 and the male rotor shaft 21 are integrally connected by the key 41 that functions as a coupling member.
  • the male rotor shaft 21 also serves as the motor shaft portion 51, and the male rotor shaft 21 and the motor shaft portion 51 are configured from one shaft body.
  • the motor 6 side of the male rotor shaft 21 extends from the portion on the motor 6 side to the portion on the motor side bearing portion 13 with respect to the locking nut 23a to constitute the motor shaft portion 51.
  • a motor shaft communication hole 30 is formed inside the motor shaft portion 51.
  • the motor shaft communication hole 30 extends in the axial direction and communicates the end surface opening on the motor side bearing portion 13 side and the plurality of oil outlet holes 21d.
  • a part of the protrusion 10b is inserted into the motor shaft communication hole 30 so that the end of the protrusion 10b of the motor shaft oil supply member 10 overlaps the insertion hole 37c in the axial direction.
  • the motor shaft communication portion 39 is configured by the communication between the oil introduction hole 10c, the motor shaft communication hole 30, and the plurality of oil outlet holes 21d.
  • the lubricating oil supplied from the motor shaft oil supply port 69 connected to the motor shaft oil supply passage 85 flows through the motor shaft communication hole 30 formed in the motor shaft portion 51.
  • the lubricating oil that has flowed through the motor shaft communication hole 30 cools the motor shaft 31 and further cools the rotor 6a.
  • the lubricating oil used to cool the motor 6 through the motor shaft communication hole 30 flows out from the plurality of oil outlet holes 21d, is converted into oil mist, and the rotor 6a and stator 6b in the motor chamber 20
  • the motor 6 is cooled by adhering to the motor shaft 31.
  • the lubricating oil used for cooling the motor 6 is discharged out of the motor chamber 20 through the intermediate oil discharge port 66, and is recovered by the oil recovery unit 71 through the intermediate oil discharge path 92.
  • the motor side oil discharge port 78 (shown in FIG. 2) on the motor side on the motor side bearing portion 13 side is closed, and the lubricating oil is discharged outside the motor chamber 20.
  • a reservoir drain hole (oil drain portion) 63 for adjusting the oil surface height of the oil stored in the oil reservoir 50 is formed.
  • the motor side oil outlet 78 on the motor side bearing section 13 side is closed by, for example, a closing plug so that the lubricating oil does not flow out from the motor chamber oil outlet 78 on the motor side shown in FIG. It is configured.
  • the oil reservoir 50 is provided on the lower side surface portion of the stator 6b on the motor side bearing portion 13 side and the motor casing 5 (in this embodiment, the cooling jacket 8). The lower side surface portion and the bottom surface portion are formed.
  • the oil reservoir 50 stores the lubricating oil supplied into the motor chamber 20 on the motor side bearing portion 13 side through the motor chamber oil supply port 77 on the motor side.
  • a storage oil discharge port 75 communicating with the storage oil discharge path 95 is provided on a side portion of the motor casing 5 that is a side portion of the motor chamber 20 (in the present embodiment, a side portion of the cooling jacket 8), or the cooling jacket 8 and It is formed on the side of the cover 9.
  • the reservoir drain hole 63 communicates with the oil reservoir 50 and the reservoir drain port 75 and functions as an oil drain.
  • the reservoir drain hole 63 adjusts the oil level of the oil stored in the oil reservoir 50 so that the lowermost part of the air gap 6g formed between the rotor 6a and the stator 6b is immersed in the lubricating oil. ing.
  • the reservoir drain hole 63 is disposed at a position lower than the lowermost part of the air gap 6g.
  • the oil level can be adjusted by adjusting the amount of oil to be discharged through the reservoir drain hole 63. Further, the oil level of the reservoir drain hole 63 may be adjusted by the installation height (the height at which the oil overflows).
  • the reservoir drain hole 63 may extend in a substantially horizontal direction or obliquely downward.
  • the lubricating oil that flows into the motor chamber 20 and cools the motor 6 is collected and stored in the oil reservoir 50.
  • the lubricating oil stored in the oil storage section 50 is adjusted by the storage oil discharge hole 63 so as to have a desired oil level height, and is discharged to the outside of the motor chamber 20. Therefore, the oil level of the lubricating oil stored in the oil reservoir 50 can be positioned slightly above the lowermost air gap 6g. As a result, the rotor 6a can be cooled using heat exchange with the lubricating oil in contact with the cooled stator 6b. On the other hand, the oil level can be adjusted to be slightly below the lowermost air gap 6g.
  • the lubricating oil is prevented from entering the air gap 6g, whereby the rotor 6a rotates smoothly and the occurrence of rotation loss can be suppressed. Moreover, since the lower part of the stator 6b is cooled by the lubricating oil stored in the oil storage part 50, the cooling effect of the motor 6 can be enhanced. Then, the lubricating oil discharged to the outside of the motor chamber 20 through the storage drain oil hole 63 is recovered by the oil recovery unit 71 through the storage drain oil passage 95.
  • the rotor shaft 21 of the screw rotor 3 and the motor shaft 31 of the motor 6 are configured separately, or as shown in the second embodiment, the male rotor shaft 21 is a motor.
  • the male rotor shaft 21 and the motor shaft portion 51 may also be configured from a single shaft body that also serves as the shaft portion 51.
  • the oil recovery unit 71 may be a space for recovering at least the lubricating oil discharged out of the motor chamber 20.
  • the oil recovery unit 71 may be configured with an oil tank separately installed outside the motor chamber 20, or may be configured with an integral structure with the motor casing 5.
  • the key 41 is used as a coupling member for integrally connecting the motor shaft 31 and the male rotor shaft 21.
  • a taper ring also referred to as spun ring
  • the taper ring connects the motor shaft 31 and the male rotor shaft 21 by using a frictional force generated on the peripheral surface of the ring disposed in the mounting space between the motor shaft 31 and the male rotor shaft 21.
  • the taper ring is configured by combining a wedge-shaped inner ring having one inclined surface and a wedge-shaped outer ring having the other inclined surface engaged with the one inclined surface.
  • the screw compressor 1 having the cooling structure described above is, for example, an oil-free type that is rotationally driven at a high speed of about 20000 rpm, and cooling oil is introduced into the rotor chamber 17 and is rotationally driven at a low speed of about 3000 rpm. It may be an oil-cooled type.
  • the cooling jacket 8 may be eliminated, and the cooling passage 8b for flowing lubricating oil for cooling the stator 6b of the motor 6 may be formed in the motor casing body 5a.
  • the stator 6b is directly attached to the inner wall surface of the motor casing body 5a.
  • the “rotor side” in the “rotor side bearing portion 11, the rotor side bearing oil supply passage 81 and the rotor side bearing oil discharge passage 91” and the like in this specification is on the screw rotor 3 side of the compressor body 2. It does not mean that the motor 6 is on the rotor 6a side.
  • the screw compressor 1 is a compressor in which a pair of male and female screw rotors 3 arranged in the horizontal direction and meshing with each other are accommodated in the rotor chamber 17 of the rotor casing 4.
  • the main body 2, the rotor 6a and the stator 6b are accommodated in the motor chamber 20 of the motor casing 5, and the motor 6 that rotationally drives the rotor shaft 21 of the screw rotor 3 by the motor shaft 31 fixed to the rotor 6a.
  • the lubricating oil supplied to the intermediate bearing portion 12 and guided into the motor chamber 20 is transmitted through the motor shaft 31 to cool the motor shaft 31.
  • Lubricating oil transmitted through the motor shaft 31 is converted into oil mist by the motor shaft 31 and the rotor 6a that rotate in the motor chamber 20, and adheres to the rotor 6a, the stator 6b, and the motor shaft 31 in the motor chamber 20. Then, the motor 6 is cooled.
  • the lubricating oil used for cooling is collected in the oil collecting unit 71, and cooling of the motor 6 is not hindered. Therefore, the motor 6 that rotationally drives the screw rotor 3 can be effectively cooled by the lubricating oil supplied to the intermediate bearing portion 12.
  • This invention can have the following features in addition to the above features.
  • the screw compressor 1 extends coaxially with respect to the rotor shaft 21 and the rotor side bearing portion 11 provided on the opposite side of the intermediate bearing portion 12 in order to support the rotor shaft 21 at both ends.
  • a motor side bearing portion 13 configured to support the motor shaft 31 and the motor chamber on the motor side bearing portion 13 side to store the lubricating oil supplied to the motor side bearing portion 13.
  • the oil reservoir 50 formed in the lower portion of the oil tank 20 and the oil drain hole are used to adjust the oil level of the oil stored in the oil reservoir 50 by discharging the lubricating oil outside the motor chamber 20.
  • a reservoir drain hole is further provided.
  • the lubricating oil stored in the oil storage section 50 is adjusted by the storage oil drain hole 63 so as to have a desired oil level height, and is discharged outside the motor chamber 20. Therefore, the oil level of the lubricating oil stored in the oil reservoir 50 can be positioned slightly above the lowermost air gap 6g. As a result, the rotor 6a can be cooled using heat exchange with the lubricating oil in contact with the cooled stator 6b. On the other hand, the oil level can be adjusted to be slightly below the lowermost air gap 6g. In that case, the lubricating oil is prevented from entering the air gap 6g, whereby the rotor 6a rotates smoothly and the occurrence of rotation loss can be suppressed. Moreover, since the lower part of the stator 6b is cooled by the lubricating oil stored in the oil storage part 50, the cooling effect of the motor 6 can be enhanced.
  • the discharge side of the rotor casing 4 is connected to the motor casing 5.
  • the motor shaft 31 of the motor 6 extends to the discharge side of the rotor casing 4.
  • the discharge side of the rotor casing 4 becomes high temperature by gas compression by the screw rotor 3, and the motor shaft 31 also becomes high temperature. Cooling the motor shaft 31 at a high temperature with the lubricating oil makes the cooling effect of the lubricating oil more remarkable.
  • an intermediate communication portion 54 for communicating with the motor chamber 20 is provided.
  • the low-pressure stage screw rotor 3 includes the intermediate communication portion 54 when the discharge side of the low-pressure stage has a negative pressure.
  • the inflow of lubricating oil into the rotor chamber 17 can be effectively prevented.
  • the intermediate bearing portion 12 includes a radial bearing 12a provided on the screw rotor 3 side and a thrust bearing 12b provided on the motor side. Between the radial bearing 12a and the thrust bearing 12b, An intermediate oil supply passage 82 for supplying lubricating oil to the intermediate bearing portion 12 is provided. According to this configuration, by providing the thrust bearing 12b on the motor side, it is possible to receive a thrust load by the thrust bearing 12b even if the rotor shaft 21 extends due to thermal expansion.
  • the motor side bearing portion 13 is assembled to the motor 6 so as to allow sliding in the axial direction on the outer ring. According to the said structure, even if the motor shaft 31 expand
  • An oil cooler 72 is provided in the middle of an oil supply passage 80 for supplying lubricating oil from the oil recovery unit 71 to the oil supply destination. According to the said structure, lubricating oil can be circulated and used.
  • the oil supply passage 80 includes a jacket oil supply passage 84 connected to a cooling jacket 8 that cools the stator 6 b of the motor 6, and a downstream side of the cooling jacket 8 is connected to the oil recovery portion 71. According to this configuration, the lubricating oil that lubricates and cools the bearing portions 11, 12, and 13 can be used for cooling the stator 6 b of the motor 6.
  • the oil supply passage 80 further includes motor chamber oil supply passages 83 and 86 connected to motor chamber oil supply ports 65 and 77 for supplying lubricating oil from the upper portion of the motor chamber 20. According to this configuration, the lubricating oil that lubricates and cools the bearing portions 11, 12, and 13 can be used as oil mist for cooling the motor 6.
  • Screw compressor oil-free screw compressor
  • Compressor body 3 Screw rotor 3a: Male rotor 3b: Female rotor 4: Rotor casing 5: Motor casing 5a: Motor casing body 6: Motor 6a: Rotor 6b: Stator 6g: Air gap 7: Bearing casing 8 : Cooling jacket 9: Cover 10: Motor shaft oil supply member 10c: Oil introduction hole 11: Rotor side bearing portion 12: Intermediate bearing portion 13: Motor side bearing portion 14a: Intermediate shaft sealing portion 17: Rotor chamber 20: Motor chamber 21: Male rotor shaft (rotor shaft) 21c: Oil guide hole 21d: Oil outlet hole 22: Female rotor shaft (rotor shaft) 26: Screw hole 27: Fastening flange 28: Fastening bolt (fastening member) 30: Motor shaft communication hole 31: Motor shaft 33: Center hole 37: Bearing support 39: Motor shaft communication part 41: Key (coupling member) 42: Keyway 50: Oil storage part 51: Motor shaft part 54: Intermediate communication part 63: Storage oil discharge hole (o

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

Abstract

L'invention concerne un compresseur à vis qui comprend : un corps de compresseur (2) ayant une paire mâle et femelle de rotors à vis (3) reçus à l'intérieur d'une chambre de rotor (17) ; un moteur (6) ayant un rotor (6a) et un stator (6b), qui sont reçus à l'intérieur d'une chambre de moteur (20), le moteur (6) entraînant en rotation l'arbre de rotor (21) d'un rotor à vis à l'aide d'un arbre de moteur (31) fixé au rotor ; un passage de distribution d'huile (80) pour distribuer de l'huile de lubrification à une partie à laquelle l'huile de lubrification doit être distribuée ; une section de palier intermédiaire (12) disposée sur le côté moteur afin de porter l'arbre de rotor ; des sections d'évacuation d'huile (66, 78) pour évacuer de l'huile de lubrification à l'extérieur de la chambre de moteur, l'huile de lubrification étant celle qui a été introduite dans la chambre de moteur par l'intermédiaire du passage de distribution d'huile ; une section de récupération d'huile (71) pour récupérer l'huile de lubrification évacuée par les sections d'évacuation d'huile.
PCT/JP2016/075512 2015-09-29 2016-08-31 Compresseur à vis WO2017056837A1 (fr)

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JP2015-191659 2015-09-29
JP2015191659A JP6467324B2 (ja) 2015-09-29 2015-09-29 スクリュ圧縮機

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US20190260272A1 (en) * 2018-02-21 2019-08-22 Honda Motor Co., Ltd. Cooling structure of driving device
CN114033678A (zh) * 2021-12-03 2022-02-11 北京航天石化技术装备工程有限公司 无润滑油脂窜漏的高洁净度电动回转容积泵及工作方法

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JP7111054B2 (ja) * 2019-04-23 2022-08-02 トヨタ自動車株式会社 車両用電動機の軸受の潤滑機構
CN111502877A (zh) * 2020-04-21 2020-08-07 四川航天中天动力装备有限责任公司 一种微型涡喷发动电动燃油泵折回式散热结构

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CN110171281B (zh) * 2018-02-21 2022-04-15 本田技研工业株式会社 驱动装置的冷却结构
CN114033678A (zh) * 2021-12-03 2022-02-11 北京航天石化技术装备工程有限公司 无润滑油脂窜漏的高洁净度电动回转容积泵及工作方法

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JP2017066935A (ja) 2017-04-06
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TW201713857A (zh) 2017-04-16
JP6467324B2 (ja) 2019-02-13
TWI611106B (zh) 2018-01-11

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