WO2018135444A1 - Oil-cooled screw compressor - Google Patents

Oil-cooled screw compressor Download PDF

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Publication number
WO2018135444A1
WO2018135444A1 PCT/JP2018/000855 JP2018000855W WO2018135444A1 WO 2018135444 A1 WO2018135444 A1 WO 2018135444A1 JP 2018000855 W JP2018000855 W JP 2018000855W WO 2018135444 A1 WO2018135444 A1 WO 2018135444A1
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WO
WIPO (PCT)
Prior art keywords
discharge
bearing portion
oil
side bearing
space
Prior art date
Application number
PCT/JP2018/000855
Other languages
French (fr)
Japanese (ja)
Inventor
貴徳 今城
透 野口
広宣 坂口
孝二 田中
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 CN201880007143.1A priority Critical patent/CN110168226B/en
Publication of WO2018135444A1 publication Critical patent/WO2018135444A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—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
    • F04C29/02—Lubrication; Lubricant separation

Definitions

  • the present invention relates to an oil-cooled screw compressor.
  • oil agitation loss is an important problem, and among the oil agitation loss, the agitation loss in the bearing portion of the screw rotor is the main factor.
  • the bearing portion of the compressor is cooled and lubricated by oil and has a structure through which oil always passes.
  • the bearing portion on the discharge side is usually cooled and lubricated by the oil that seals the shaft seal portion, it is difficult to adjust the amount of oil. Therefore, in the bearing part on the discharge side, unlike the oil bath state assumed by the bearing manufacturer, the oil level on the upstream side of the bearing part rises due to the resistance to the oil flow by the bearing part. The contact area with the bearing portion increases, and the oil agitation loss increases.
  • Patent Document 1 discloses an oil discharge structure of a bearing portion of an oil-cooled screw compressor.
  • an annular space is provided in the outer ring restraining sleeve of the bearing portion, thereby preventing oil agitation loss due to accumulation of oil in the space on the downstream side of the bearing portion.
  • an object of the present invention is to provide an oil-cooled screw compressor that can reduce oil agitation loss on the upstream side of the bearing portion.
  • One aspect of the present invention is a pair of screw rotors in which an oil-cooled screw compressor rotates in an engaged state to compress gas,
  • a casing for accommodating the pair of screw rotors;
  • a discharge-side bearing portion that supports a discharge-side rotor shaft of the screw rotor;
  • a shaft seal portion for sealing the discharge-side rotor shaft;
  • a first space provided between the shaft sealing portion and the discharge-side bearing portion;
  • a second space provided between an axial end of the discharge side bearing portion and the casing;
  • a communication passage formed in the casing and communicating with the first space and the second space is provided.
  • the aspect further includes the following configuration.
  • the contact lower end of the portion of the communication passage in contact with the discharge side bearing portion is between the lowermost end of the inner ring transfer surface of the discharge side bearing portion and the lower end of the outer ring transfer surface of the discharge side bearing portion. positioned.
  • the lower end of the portion of the communication passage that is in contact with the discharge-side bearing portion is disposed between the lowermost end of the inner ring transfer surface and the lowermost end of the outer ring transfer surface of the discharge-side bearing portion.
  • the oil surface position in one space can be maintained at a height at which the rolling elements bathe, and excess oil can be moved to the second space by the communication passage while supplying the required amount of oil to the bearing portion. .
  • the lower end of the contact is located between the lowermost end of the orbital circle at the center of the rolling element of the discharge side bearing portion and the lowermost end of the outer ring transfer surface of the discharge side bearing portion. is doing.
  • the lower end of the contact of the communication passage is disposed between the lowermost end of the orbital circle at the center of the rolling element of the discharge-side bearing portion and the lowermost end of the outer ring transfer surface.
  • the oil level position can be further maintained between the center position of the rolling elements and the outer ring transfer surface, and excess oil is supplied to the second space by the communication passage while supplying a necessary and smaller amount of oil to the bearing portion. Can be moved.
  • the discharge port for discharging the compressed gas compressed by the pair of screw rotors is disposed below or laterally with respect to a straight line connecting the axis of the discharge side rotor shaft,
  • the communication passage is a surface perpendicular to the direction of the gas acting force acting on the discharge side rotor shaft by the compressed gas, and passes through the axis of the discharge side rotor shaft, and the discharge port with respect to the gas acting force surface On the side.
  • the discharge-side rotor shaft receives a force from the compressed gas.
  • the communication passage on the discharge port side with respect to the gas action force surface, that is, on the opposite side of the direction of the gas action force received from the compressed gas, the support force of the discharge side bearing portion by the casing is reduced. And a communication passage can be provided.
  • the communication passage is provided in a predetermined range on the opposite side of the direction of the gas acting force received from the compressed gas, so that the communication without reducing the supporting force of the discharge side bearing portion by the casing.
  • a passage can be provided.
  • the communication passage extends in a straight line and has a longitudinal axis parallel to the discharge-side rotor shaft.
  • the connecting passage when the connecting passage is manufactured by machining, the connecting passage can be manufactured by one machining from the outside of the casing. Can do. Even when the communication passage is made of cast metal, it has a simple structure, so it can be manufactured by simply modifying a part of the bearing holding hole mold without considering the mold removal direction. Further, the manufacturability and the manufacturing cost of the communication passage can be advantageous.
  • a plurality of communication passages are provided.
  • the oil level position is increased by providing a plurality of communication passages. It can be prevented from rising.
  • a second aspect of the present invention includes a pair of screw rotors that rotate in an engaged state and compress gas.
  • a casing for accommodating the pair of screw rotors;
  • a suction side bearing portion that supports a suction side rotor shaft of the screw rotor;
  • a third space provided between the axial end of the suction side bearing portion and the casing;
  • a second communication passage formed in the casing and communicating the third space and the suction space is provided.
  • the second aspect preferably further comprises the following configuration.
  • the lower end of the contact portion of the second communication passage that is in contact with the suction side bearing portion is the lowermost end of the inner ring transfer surface of the suction side bearing portion and the lowermost end of the outer ring transfer surface of the suction side bearing portion. Located between.
  • the lower end of the contact is located between the lowermost end of the orbital circle at the center of the rolling element of the suction side bearing portion and the lowermost end of the outer ring transfer surface of the suction side bearing portion. is doing.
  • the contact lower end of the second communication passage is arranged between the lowermost end of the orbital circle at the center of the rolling element of the suction side bearing portion and the lowermost end of the outer ring transfer surface, whereby the third The oil surface position of the space can be maintained between the center position of the rolling elements and the outer ring transfer surface, and excess oil can be removed by the second communication passage while supplying a necessary and smaller amount of oil to the bearing portion. It can be moved to the suction space.
  • the discharge port for discharging the compressed gas compressed by the pair of screw rotors is disposed below or laterally with respect to a straight line connecting the axis of the suction side rotor shaft,
  • the second communication passage is a surface perpendicular to the direction of the gas acting force acting on the suction side rotor shaft by the compressed gas, and passes through the axial center of the suction side rotor shaft and the gas acting force surface. It is provided on the discharge port side.
  • the suction-side rotor shaft receives a force from the compressed gas.
  • the second communication passage on the discharge port side with respect to the gas acting force surface, that is, on the opposite side of the direction of the gas acting force received from the compressed gas, the supporting force of the suction side bearing portion by the casing is reduced. Without this, the second communication passage can be provided.
  • the second communication passage includes a first inclined line that passes through the axis and forms an angle of 45 degrees downward with respect to an anti-gas action force line extending in a direction opposite to the gas action force with respect to the axis. , And a second inclined line having an angle of 45 degrees upward with respect to the anti-gas acting force line.
  • the second communication passage by providing the second communication passage in a predetermined range opposite to the direction of the gas acting force received from the compressed gas, the supporting force of the suction side bearing portion by the casing is not reduced.
  • a second communication passage can be provided.
  • the second communication passage extends linearly and has a longitudinal axis parallel to the suction-side rotor shaft.
  • the second connecting passage when the second connecting passage is manufactured by machining, the second connecting passage can be manufactured by one machining from the outside of the casing. Can be advantageous. Even if the second communication passage is made of cast metal, it has a simple structure, so it can be made by simply modifying a part of the bearing holding hole mold without considering the mold removal direction. Thus, the manufacturability and manufacturing cost of the second communication passage can be advantageous.
  • a plurality of the second communication passages are provided.
  • the oil level position is determined by providing a plurality of second communication passages. It is possible to prevent a large rise.
  • a third aspect of the present invention comprises a pair of screw rotors that rotate in mesh and compress gas.
  • a casing for accommodating the pair of screw rotors;
  • a discharge-side bearing portion that supports a discharge-side rotor shaft of the screw rotor;
  • a shaft seal portion for sealing the discharge-side rotor shaft;
  • a first space provided between the shaft sealing portion and the discharge-side bearing portion;
  • a second space provided between an axial end of the discharge side bearing portion and the casing;
  • a suction side bearing portion that supports a suction side rotor shaft of the screw rotor;
  • a third space provided between the axial end of the suction side bearing portion and the casing;
  • the communication passage and the second communication passage are provided at positions overlapping each other when
  • the communication passage and the second communication passage are provided at positions overlapping each other when viewed from the axial direction of the screw rotor, both the supporting forces of the discharge side bearing portion and the suction side bearing portion by the casing are shared.
  • the communication passage and the second communication passage can be provided without being lowered.
  • an oil-cooled screw compressor that can reduce oil agitation loss on the upstream side of the bearing can be provided.
  • FIG. 2 is a partial sectional view taken along line II-II in FIG.
  • FIG. 3 is a partial sectional view taken along line III-III in FIG. 1.
  • FIG. 4 is a partial cross-sectional view along IV-IV in FIG. 1.
  • the fragmentary sectional view of the discharge side bearing part of the screw compressor concerning a 2nd embodiment of the present invention.
  • the fragmentary sectional view of the discharge side bearing part of the screw compressor concerning a 3rd embodiment of the present invention.
  • the fragmentary sectional view of the discharge side bearing part of a screw compressor which shows the modification of a communicating path.
  • FIG. 10 is a partial cross-sectional view taken along line XX in FIG. 9.
  • FIG. 1 is a partial plan view of a plane of an oil-cooled screw compressor 2 according to the first embodiment of the present invention.
  • 2 is a partial cross-sectional view taken along line II-II in FIG. 1
  • FIG. 3 is a partial cross-sectional view taken along line III-III in FIG. 1
  • FIG. 4 is a partial cross-sectional view taken along line IV-IV in FIG. It is sectional drawing.
  • the screw compressor 2 of this embodiment includes a male and female pair of male rotors 8 (screw rotors) that mesh with each other in a compression chamber 6 formed by a casing 4 made of a casting.
  • a female rotor 9 (screw rotor) is rotatably accommodated.
  • the male rotor 8 includes a male rotor body 8a that compresses air, and a suction-side rotor shaft 8b and a discharge-side rotor shaft 8c that support the male rotor body 8a.
  • the female rotor 9 includes a female rotor body 9a that meshes with the male rotor body 8a to compress air, and a suction-side rotor shaft 9b and a discharge-side rotor shaft 9c that support the female rotor body 9a.
  • the air sucked from the suction space 48 and compressed by the male rotor main body 8a and the female rotor main body 9a is discharged from the discharge port 49 and supplied to the next facility or the like through the discharge port 50.
  • a bearing chamber 10 is formed together with the compression chamber 6.
  • a shaft seal portion (discharge-side shaft seal portion) 14 is disposed to isolate the compression chamber 6 from the bearing chamber 10.
  • the bearing chamber 10 accommodates a discharge-side bearing portion 16 that rotatably supports the discharge-side rotor shafts 8c and 9c.
  • the discharge-side bearing portion 16 includes a ring-shaped inner ring 18, a ring-shaped outer ring 20, and a spherical or columnar rolling element 22 disposed therebetween.
  • the inside of the bearing chamber 10 is partitioned into a bearing upstream space (first space) 24 and a bearing downstream space (second space) 26 by the discharge-side bearing portion 16.
  • the first space 24 is defined by the shaft seal portion 14, the discharge side bearing portion 16, and the casing 4.
  • the suction side rotor shaft 8b of the male rotor 8 extends to the outside of the casing 4 and is connected to a motor or the like (not shown). Accordingly, a shaft sealing portion (not shown) is also provided at a portion where the suction side rotor shaft 8 b of the male rotor 8 passes through the casing 4.
  • end portions of the discharge-side rotor shafts 8 c and 9 c are accommodated in the casing 4.
  • a bearing inner ring restrainer 28 and a bearing outer ring restrainer 30 for receiving a thrust load are provided at the ends of the discharge-side rotor shafts 8c and 9c.
  • the bearing inner ring restraint 28 is in contact with the inner ring 18 of the discharge side bearing portion 16, and the bearing outer ring restraint 30 is in contact with the outer ring 20 of the discharge side bearing portion 16 to restrict axial movement of the inner ring 18 and the outer ring 20.
  • the second space 26 is defined by the discharge-side bearing portion 16, the casing 4, and the bearing outer ring retainer 30.
  • a rotor oil supply port 32 for supplying oil to the screw rotors 8 and 9 is provided below the casing 4.
  • the rotor refueling port 32 is provided through the casing 4 and communicates with a lower (high pressure side) portion in the compression chamber 6 after the air is trapped and compressed by the male rotor main body 8a and the female rotor main body 9a. ing.
  • the oil supplied through the rotor oil supply port 32 cools the air in the middle of compression and seals the gap to improve the compression performance.
  • the casing 4 is provided with a shaft seal oil supply port 34.
  • the shaft seal oil filler 34 is provided through the casing 4 in the same manner as the rotor oil filler 32.
  • the shaft seal oil supply port 34 communicates with a first space 24 provided between the shaft seal portion 14 and the discharge side bearing portion 16 in order to supply oil to the shaft seal portion 14 and the discharge side bearing portion 16.
  • the screw compressor 2 of the present embodiment drains the oil accumulated in the first space 24, and therefore the first space 24 and the axial end of the discharge-side bearing portion 16.
  • communication passages 44 a and 44 b communicating with the second space 26 provided between the portion and the casing 4 and the bearing outer ring retainer 30.
  • the communication passages 44a and 44b are formed by providing a cutout in the casing 4, each extending linearly and having a longitudinal axis parallel to the discharge-side rotor shafts 8c and 9c. Note that a notch 30 a is also formed in the bearing outer ring retainer 30 so that the communication passages 44 a and 44 b communicate the first space 24 and the second space 26.
  • the communication passages 44a, 44b In the cross section perpendicular to the axial direction of the discharge-side rotor shafts 8c, 9c, the communication passages 44a, 44b have an arc shape.
  • the contact lower ends 44a1 and 44b1 of the portions of the communication passages 44a and 44b that are in contact with the discharge-side bearing portion 16 have the lowermost end 18a of the inner ring transfer surface of the inner ring 18 of the discharge-side bearing portion 16 in the vertical direction. And the lowermost end 20a of the outer ring transfer surface of the outer ring 20 of the discharge side bearing portion 16. More specifically, the contact lower ends 44a1 and 44b1 are located between the lowermost end 22a1 of the orbital circle 22a at the center of the rolling element 22 of the discharge side bearing portion 16 and the lowermost end 20a of the outer ring transfer surface of the discharge side bearing portion 16. positioned.
  • the discharge-side rotor shafts 8c and 9c act in directions away from each other due to the force received from the compressed gas. This force, that is, the gas acting force is received by the discharge side bearing portion 16, and the discharge side bearing portion 16 is held by the casing 4.
  • the discharge-side rotor shafts 8c and 9c are arranged side by side in the horizontal direction.
  • the line connecting the shaft centers 8c1 and 9c1 of the discharge-side rotor shafts 8c and 9c makes an angle of 0 degrees with respect to the horizontal line S.
  • the discharge port 49 exists below the line connecting the shaft centers 8c1 and 9c1 of the discharge-side rotor shafts 8c and 9c.
  • the gas acting force F1 on the discharge-side rotor shaft 8c side is on an axis center line L1 passing through the shaft center 8c1 of the discharge-side rotor shaft 8c and the shaft center 9c1 of the discharge-side rotor shaft 9c, and the shaft center 8c1.
  • a line L1a extending through the axis 9c1 on the opposite side is directed in a direction inclined by an angle ⁇ 1 in a direction opposite to the compressed gas discharge direction (vertically downward).
  • the angle ⁇ 1 is about 60 degrees.
  • the gas acting force F2 on the discharge-side rotor shaft 9c side is compressed gas discharge with respect to a line L1b extending on the shaft center line L1 and passing through the shaft center 9c1 on the opposite side to the shaft center 8c1.
  • the direction (vertically below) is directed in a direction inclined by an angle ⁇ 2 in the opposite direction.
  • the angle ⁇ 2 is about 60 degrees.
  • the communication passage 44a is a surface perpendicular to the direction of the gas action force F1, is below the gas action force surface S1 passing through the axis 8c1, and is opposite to the direction of the gas action force F1 (on the discharge port 49 side). Is provided.
  • the communication passage 44a passes through the axis 8c1 and forms a first inclined line F1′a and an antigas action force line F1 ′ that form an angle of 45 degrees downward with respect to the antigas action force line F1 ′. Is provided in a range sandwiched between the second inclined line F1′b and an angle of 45 degrees upward.
  • an anti-gas action force line F1 'passing through the axis 8c1 and extending in the opposite direction to the gas action force F1 and the axis 8c1 is referred to as an anti-gas action force line F1'.
  • the communication passage 44b is a surface perpendicular to the direction of the gas action force F2, is below the gas action force surface S2 passing through the axis 9c2, and is opposite to the direction of the gas action force F2 (on the discharge port 49 side). Is provided.
  • the communication passage 44b passes through the axis 9c1 and forms a first inclined line F2′a and an antigas action force line F2 ′ that form an angle of 45 degrees downward with respect to the antigas action force line F2 ′. Is provided in a range sandwiched between the second inclined line F2′b and an angle of 45 degrees upward.
  • an anti-gas action force line F2 'passing through the axis 9c1 and extending in the opposite direction to the gas action force F2 and the axis 9c1 is referred to as an anti-gas action force line F2'.
  • the screw compressor 2 of the present embodiment drains the oil accumulated in the second space 26, so that one end of the screw compressor communicates with the second space 26.
  • a passage 46 is provided.
  • the other end of the oil discharge passage 46 communicates with the tooth groove portion 8e after the male rotor body 8a and the female rotor body 9a of the compression chamber 6 are closed (the tooth groove portion of the female rotor body 9a is not shown).
  • the oil discharged from the second space 26 is supplied to the tooth groove portions 8e of the male rotor main body 8a and the female rotor main body 9a.
  • the oil discharge destination of the oil discharge passage 46 is provided closer to the suction end surfaces 8 f and 9 f (right side in the drawing) of the male rotor main body 8 a and the female rotor main body 9 a than the rotor oil supply port 32.
  • the suction end faces 8f and 9f are end faces provided on the suction side of the male rotor main body 8a and the female rotor main body 9a.
  • the male rotor body 8a and the female rotor body 9a are connected to the suction side rotor shafts 8b and 9b at the suction end faces 8f and 9f, respectively.
  • the discharge-side rotor shafts 8c and 9c receive a force from the compressed gas.
  • the casing 4 The communication passages 44a and 44b can be provided without reducing the supporting force of the discharge-side bearing portion 16 due to the above.
  • the communication passages 44a and 44b pass through a predetermined range opposite to the direction of the gas acting forces F1 and F2 received from the compressed gas, that is, the shaft centers 8c1 and 9c1, and the antigas acting force lines F1 ′ and F2 ′.
  • the first inclined lines F1′a and F2′a that form an angle of 45 ° downward with respect to the second and the second inclined lines F1 that form an angle of 45 ° with respect to the anti-gas acting force lines F1 ′ and F2 ′. It is provided in a range sandwiched between 'b and F2'b.
  • the communication passages 44a and 44b extend linearly and have a longitudinal axis parallel to the discharge-side rotor shafts 8c and 9c.
  • the connecting passages 44a and 44b can be manufactured by a single machining from the outside of the casing 4, so that the manufacturability and manufacturing cost of the connecting passages 44a and 44b can be advantageous.
  • the communication passages 44a and 44b are made of cast metal, since the structure is simple, it is possible to manufacture by simply remodeling a part of the bearing holding hole mold without considering the mold drawing direction. It is possible, and the manufacturability and manufacturing cost of the communication passages 44a and 44b can be advantageous.
  • FIG. 5 is a partial cross-sectional view of the discharge-side bearing portion 16 of the screw compressor 2 according to the second embodiment of the present invention.
  • the discharge-side rotor shafts 8c and 9c are arranged side by side in the vertical direction. That is, in the present embodiment, a line connecting the shaft centers 8c1 and 9c1 of the discharge-side rotor shafts 8c and 9c forms an angle of 90 degrees with respect to the horizontal line. Therefore, the present embodiment is different from the first embodiment in which the discharge-side rotor shafts 8c and 9c are arranged side by side in the horizontal direction, and the arrangement of the discharge-side rotor shafts 8c and 9c. The configuration is substantially the same as in the first embodiment.
  • the contact lower ends 44a1 and 44b1 of the portions of the communication passages 44a and 44b that are in contact with the discharge-side bearing portion 16 have the lowermost end 18a of the inner ring transfer surface of the inner ring 18 of the discharge-side bearing portion 16 in the vertical direction. And the lowermost end 20a of the outer ring transfer surface of the outer ring 20 of the discharge side bearing portion 16.
  • the contact lower ends 44a1 and 44b1 are located between the lowermost end 22a1 of the orbital circle 22a at the center of the rolling element 22 of the discharge side bearing portion 16 and the lowermost end 20a of the outer ring transfer surface of the discharge side bearing portion 16. positioned.
  • the discharge-side rotor shafts 8c and 9c act in directions away from each other due to the force received from the compressed gas.
  • This force that is, the gas acting forces F ⁇ b> 1 and F ⁇ b> 2 are received by the discharge side bearing portion 16, and the discharge side bearing portion 16 is held by the casing 4.
  • the discharge port 49 exists on the right side of the line connecting the shaft centers 8c1 and 9c1 of the discharge-side rotor shafts 8c and 9c.
  • the gas acting force F1 on the discharge-side rotor shaft 8c side is on an axis center line L1 passing through the shaft center 8c1 of the discharge-side rotor shaft 8c and the shaft center 9c1 of the discharge-side rotor shaft 9c, and the shaft center 8c1.
  • the line L1a extending through the axis 9c1 on the opposite side passes through the direction inclined by the angle ⁇ 3 in the direction opposite to the compressed gas discharge direction (rightward).
  • the angle ⁇ 3 is about 60 degrees.
  • the gas acting force F2 on the discharge-side rotor shaft 9c side is compressed gas discharge with respect to a line L1b extending on the shaft center line L1 and passing through the shaft center 9c1 on the opposite side to the shaft center 8c1. It is directed in a direction inclined by an angle ⁇ 4 in a direction opposite to the direction (right side).
  • the angle ⁇ 4 is about 60 degrees.
  • the communication passage 44a is a surface perpendicular to the direction of the gas acting force F1 and passes through the axis 8c1 and is opposite to the direction of the gas acting force F1 of the gas acting force surface S1 (on the right side, on the discharge port 49 side). ).
  • the communication passage 44b is a surface perpendicular to the direction of the gas acting force F2, and passes through the shaft center 9c1 and is opposite to the direction of the gas acting force F2 of the gas acting force surface S2 (on the right side, the discharge port 49 side). ).
  • the discharge-side rotor shafts 8c and 9c are adapted to receive a force from the compressed gas.
  • the communication passages 44a and 44b can be provided without reducing the supporting force of the discharge-side bearing portion 16 by the casing 4.
  • FIG. 6 is a partial cross-sectional view of the discharge-side bearing portion 16 of the screw compressor 2 according to the third embodiment of the present invention.
  • the discharge-side rotor shafts 8c and 9c are arranged obliquely in the vertical direction. That is, in the present embodiment, the line connecting the shaft centers 8c1 and 9c1 of the discharge-side rotor shafts 8c and 9c makes an angle of 45 degrees with respect to the horizontal line S.
  • this embodiment includes the first embodiment in which the discharge-side rotor shafts 8c and 9c are arranged in a horizontal direction and the second embodiment in which the discharge-side rotor shafts 8c and 9c are arranged in a vertical direction,
  • the arrangement differs in the way of arranging the discharge-side rotor shafts, and the configuration of the other parts is substantially the same as in the first embodiment disassembly.
  • the contact lower ends 44a1 and 44b1 of the portions of the communication passages 44a and 44b that are in contact with the discharge-side bearing portion 16 have the lowermost end 18a of the inner ring transfer surface of the inner ring 18 of the discharge-side bearing portion 16 in the vertical direction. And the lowermost end 20a of the outer ring transfer surface of the outer ring 20 of the discharge side bearing portion 16.
  • the contact lower ends 44a1 and 44b1 are located between the lowermost end 22a1 of the orbital circle 22a at the center of the rolling element 22 of the discharge side bearing portion 16 and the lowermost end 20a of the outer ring transfer surface of the discharge side bearing portion 16. positioned.
  • the discharge-side rotor shafts 8c and 9c act in directions away from each other due to the force received from the compressed gas.
  • This force that is, the gas acting forces F ⁇ b> 1 and F ⁇ b> 2 are received by the discharge side bearing portion 16, and the discharge side bearing portion 16 is held by the casing 4.
  • the discharge port 49 exists on the lower right side of the line connecting the shaft centers 8c1 and 9c1 of the discharge-side rotor shafts 8c and 9c. ing.
  • the gas acting force F1 on the discharge-side rotor shaft 8c side is on an axis center line L1 passing through the shaft center 8c1 of the discharge-side rotor shaft 8c and the shaft center 9c1 of the discharge-side rotor shaft 9c, and the shaft center 8c1.
  • the line L1a that passes through the axis 9c1 on the opposite side passes through the direction inclined by the angle ⁇ 5 in the direction opposite to the compressed gas discharge direction (lower right).
  • the angle ⁇ 5 is about 60 degrees.
  • the gas acting force F2 on the discharge-side rotor shaft 9c side is compressed gas discharge with respect to a line L1b extending on the shaft center line L1 and passing through the shaft center 9c1 on the opposite side to the shaft center 8c1. It faces the direction inclined by an angle ⁇ 6 in the opposite direction to the direction (lower right).
  • the angle ⁇ 6 is about 60 degrees.
  • the communication passage 44a is a surface perpendicular to the direction of the gas acting force F1 and is located on the lower right side of the gas acting force surface S1 passing through the axis 8c1 and in the direction opposite to the direction of the gas acting force F1 (on the discharge port 49 side ).
  • the communication passage 44a passes through the axial center 8c1 and is inclined with respect to the first inclined line L5a and the anti-gas action force line F1 ′ that form an angle of 45 degrees downward with respect to the anti-gas action force line F1 ′. And a second slope line L5b that forms an angle of 45 degrees upward.
  • an anti-gas action force line F1 'passing through the axis 8c1 and extending in the opposite direction to the gas action force F1 and the axis 8c1 is referred to as an anti-gas action force line F1'.
  • the communication passage 44b is a surface perpendicular to the direction of the gas action force F2, is below the gas action force surface S2 passing through the axis 9c2, and is opposite to the direction of the gas action force F2 (on the discharge port 49 side). Is provided.
  • the communication passage 44b passes through the shaft center 9c1 and is inclined with respect to the first inclined line L6a and the anti-gas action force line F2 ′ that form an angle of 45 degrees downward with respect to the anti-gas action force line F2 ′. And a second inclined line L6b that forms an angle of 45 degrees upward.
  • an anti-gas action force line F2 'passing through the axis 9c1 and extending in the opposite direction to the gas action force F2 and the axis 9c1 is referred to as an anti-gas action force line F2'.
  • the discharge-side rotor shafts 8c and 9c are adapted to receive a force from the compressed gas.
  • the communication passages 44a and 44b are provided on the side opposite to the direction of the gas acting forces F1 and F2 received from the compressed gas.
  • the communication passages 44a and 44b can be provided without reducing the supporting force of the discharge-side bearing portion 16 by the casing 4.
  • the communication passages 44a and 44b pass through a predetermined range opposite to the direction of the gas acting forces F1 and F2 received from the compressed gas, that is, through the shaft centers 8c1 and 9c1 and to the antigas acting force lines F1 ′ and F2 ′.
  • the second inclined lines L5b and L6b that form an angle of 45 degrees upward It is provided in the range to be sandwiched.
  • the communication passages 44a and 44b in the cross section perpendicular to the axial direction of the discharge-side rotor shafts 8c and 9c, have an arc shape.
  • the size of the communication passage is not particularly limited, and may be larger or smaller than the communication passage shown in the first to third embodiments.
  • a plurality of communication passages 44a may be provided. In this case, the contact lower end 44a1 of the portion in contact with the discharge side bearing portion 16 of the at least one communication passage 44a has the lowermost end 18a of the inner ring transfer surface of the inner ring 18 of the discharge side bearing portion 16 and the discharge side bearing portion in the vertical direction.
  • the outer ring 20 is positioned between the lowermost ends 20a of the outer ring transfer surfaces of the sixteen outer rings 20.
  • the contact lower end 44a1 of the at least one communication passage 44a has the lowermost end 22a1 of the track circle 22a at the center of the rolling element 22 of the discharge side bearing portion 16 and the outer ring transfer surface of the discharge side bearing portion 16. More preferably, it is located between the lowermost end 20a.
  • the amount of movement of oil from the first space 24 to the second space 26 can be adjusted, and as a result, the position of the oil surface can be adjusted to an appropriate position.
  • FIG. 9 is a plan partial sectional view of the oil-cooled screw compressor 2 when a communication passage is provided on the suction side.
  • 10 is a partial cross-sectional view taken along line XX of FIG.
  • Another embodiment is different from the first to third embodiments in that a communication passage is provided on the suction side, and the other configurations are the same as those of the first to third embodiments. For this reason, in the description of this modification, the same reference numerals are given to the same portions as those in the above-described embodiment, and detailed descriptions thereof are omitted.
  • a suction side bearing chamber 11 is formed in the casing 4 together with the compression chamber 6 and the bearing chamber 10.
  • a suction side shaft sealing portion 39 is disposed between the suction side rotor shafts 8 b and 9 b and the casing 4, and isolates the compression chamber 6 from the suction side bearing chamber 11.
  • the suction side bearing chamber 11 accommodates a suction side bearing portion 35 that rotatably supports the suction side rotor shafts 8b and 9b.
  • the suction-side bearing portion 35 includes a ring-shaped inner ring, a ring-shaped outer ring, and a spherical or cylindrical rolling element disposed therebetween. Then, the suction side bearing portion 35 divides the inside of the suction side bearing chamber 11 into a third space 38 provided between the axial end portion of the suction side bearing portion 35 and the casing 4 and a suction side shaft sealing portion 39. It has been.
  • the suction-side rotor shaft 8b of the male rotor 8 extends to the outside of the casing 4, and is connected to a motor or the like (not shown).
  • the end of the suction side rotor shaft 9 b of the female rotor 9 is accommodated in the casing 4.
  • a bearing inner ring restrainer 41 for receiving a thrust load is provided at the end of the suction side rotor shaft 9b. The bearing inner ring restraint 41 is in contact with the inner ring of the suction side bearing portion 35 and restricts the movement of the inner ring in the axial direction.
  • the casing 4 is provided with a fuel filler port 40. Similar to the shaft-sealed oil supply port 34, the oil supply port 40 is provided so as to penetrate the casing 4. The oil supply port 40 communicates with the third space 38 in order to supply oil to the suction side bearing portion 35.
  • the screw compressor 2 includes second communication passages 44 c and 44 d that connect the third space 38 and the suction space 48 in order to drain the oil accumulated in the third space 38.
  • the second communication passages 44c and 44d are formed by providing a cutout in the casing 4, each extending linearly and having a longitudinal axis parallel to the suction-side rotor shafts 8b and 9b. Yes. In the cross section perpendicular to the axial direction of the suction-side rotor shafts 8b and 9b, the second communication passages 44c and 44d have an arc shape.
  • the arrangement of the communication passages 44a and 44b described in FIGS. 4 to 8 can be similarly applied to the second communication passages 44c and 44d provided on the suction side. That is, by replacing the discharge side rotor shafts 8c and 9c shown in FIGS. 4 to 8 with the suction side rotor shafts 8b and 9b, the suction side second communication passages 44c and 44d can be similarly explained.
  • the contact lower ends 44a1 and 44b1 of the portions of the second communication passages 44c and 44d that are in contact with the suction side bearing portion 35 are located between the lowermost end 18a of the inner ring transfer surface of the suction side bearing portion 35 and the lowermost end 20a of the outer ring transfer surface.
  • the oil level position of the third space 38 can be maintained at a height at which the rolling elements 22 bathe, and the second communication passage is supplied to the suction-side bearing portion 35 while supplying the required amount of oil. Excess oil can be moved to the suction space 48 by 44c and 44d.
  • the suction side rotor shafts 8b and 9b are adapted to receive force from the compressed gas.
  • the second communication passages 44c and 44d can be provided without reducing the supporting force of the suction side bearing portion 35 by the casing 4.
  • the second communication passages 44c and 44d pass through a predetermined range on the opposite side to the direction of the gas acting forces F1 and F2 received from the compressed gas, that is, through the shaft centers 8c1 and 9c1, and the antigas acting force lines F1 ′, First inclination lines F1′a and F2′a that form an angle of 45 degrees downward with respect to F2 ′, and a second inclination that forms an angle of 45 degrees with respect to the anti-gas action force lines F1 ′ and F2 ′. It is provided in a range sandwiched between the lines F1′b and F2′b. By providing the second communication passages 44c and 44d in this range, the second communication passages 44c and 44d can be provided without reducing the support force of the suction side bearing portion 35 by the casing 4.
  • the second communication passages 44c and 44d extend linearly and have a longitudinal axis parallel to the suction side rotor shafts 8b and 9b.
  • the second connecting passages 44c and 44d can be manufactured by one machining from the outside of the casing 4, so that the manufacturability and manufacturing cost of the second connecting passages 44c and 44d are advantageous. can do.
  • the second communication passages 44c and 44d are made of cast metal, since the structure is simple, it is only necessary to modify a part of the bearing holding hole mold without considering the mold drawing direction. Manufacture is possible, and the manufacturability and manufacturing cost of the second communication passages 44c and 44d can be advantageous.
  • the suction-side rotor shafts 8b and 9b are adapted to receive a force from the compressed gas.
  • the second communication passages 44c and 44d are provided on the side opposite to the direction of the gas acting forces F1 and F2 received from the compressed gas.
  • the second communication passages 44c and 44d can be provided without reducing the supporting force of the suction side bearing portion 35 by the casing 4.
  • the suction-side rotor shafts 8b and 9b are adapted to receive a force from the compressed gas.
  • the second communication passages 44c and 44d are disposed on the opposite side of the direction of the gas acting forces F1 and F2 received from the compressed gas. By providing, the second communication passages 44c and 44d can be provided without reducing the supporting force of the suction side bearing portion 35 by the casing 4.
  • the second communication passages 44c and 44d pass through a predetermined range opposite to the direction of the gas acting forces F1 and F2 received from the compressed gas, that is, pass through the shaft centers 8c1 and 9c1, and antigas acting force lines F1 ′ and F2 First inclined lines L5a and L6a which form an angle of 45 degrees downward with respect to ', and second inclined lines L5b and L6b which form an angle of 45 degrees upward with respect to the anti-gas action force lines F1' and F2 '; , Are provided in a range between.
  • the second communication passages 44c and 44d can be provided without reducing the support force of the suction side bearing portion 35 by the casing 4.
  • the communication passages 44a and 44b are provided on the discharge side.
  • the second communication passages 44c and 44d are shown on the suction side.
  • the communication passages 44a and 44b may be provided only on the discharge side, the second communication passages 44c and 44d may be provided only on the suction side, or the communication passages may be provided on both the discharge side and the suction side. Good.
  • the communication passages 44a and 44b and the second communication passages 44c and 44d are provided at positions overlapping each other when viewed from the axial direction of the screw rotors 8 and 9. It is preferable.
  • the communication passages 44 a and 44 b and the second communication passages 44 c and 44 d can be provided without reducing both the supporting forces of the discharge side bearing portion 16 and the suction side bearing portion 35 by the casing 4.
  • the communication passages 44a and 44b and the second communication passages 44c and 44d are provided at positions overlapping each other when viewed from the axial direction of the screw rotors 8 and 9. , 44d need only partially overlap each other when viewed from the axial direction of the screw rotors 8,9.
  • the second communication passages 44c and 44d in the cross section perpendicular to the axial direction of the suction side rotor shafts 8b and 9b, have an arc shape, but as shown in FIG. You may have.
  • the size of the second communication passage is not particularly limited, and may be larger or smaller than the second communication passage shown in another embodiment.
  • a plurality of second communication passages 44c may be provided. In this case, the contact lower end 44a1 of the portion in contact with the suction side bearing portion 35 of at least one second communication passage 44c is in the vertical direction with the lowest end 18a of the inner ring transfer surface of the inner ring 18 of the suction side bearing portion 35 and the suction side.
  • the bearing portion 35 is located between the outermost ring transfer surface of the outer ring 20 and the lowermost end 20a. More specifically, the contact lower end 44a1 of at least one second communication passage 44c is connected to the lowermost end 22a1 of the track circle 22a at the center of the rolling element 22 of the suction side bearing portion 35 and the outer ring transfer of the suction side bearing portion 35. More preferably, it is located between the lowermost end 20a of the surface.
  • the amount of movement of oil from the third space 38 to the suction space 48 can be adjusted, and as a result, the position of the oil surface can be adjusted to an appropriate position. it can.

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Abstract

The present invention is characterized by comprising: a pair of screw rotors (8, 9) for compressing gas by rotating while engaging with each other; a casing (4) for accommodating the pair of screw rotors (8, 9); discharge-side bearing sections (16) for supporting the discharge-side rotor shafts (8c,9c) of the screw rotors (8, 9); shaft seal sections (14) for sealing the discharge-side rotor shafts (8c, 9c); first spaces (24) provided between the shaft seal sections (14) and the discharge-side bearing sections (16); second spaces (26) provided between the casing (4) and axial ends of the discharge-side bearing sections (16); and communication passages (44a, 44b) formed in the casing (4) and providing communication between the first spaces (24) and the second spaces (26).

Description

油冷式スクリュ圧縮機Oil-cooled screw compressor
　本発明は、油冷式スクリュ圧縮機に関する。 The present invention relates to an oil-cooled screw compressor.
　油冷式スクリュ圧縮機では、油の撹拌ロスが重要な問題となっており、油の撹拌ロスの内、スクリュロータの軸受部における撹拌ロスはその主要因である。圧縮機の軸受部は、油により冷却及び潤滑され、常に油が通過する構造となっている。そして、特に吐出側の軸受部は、通常、軸封部をシールした油によって冷却及び潤滑が行われるため、油量の調節は困難である。したがって、吐出側の軸受部では、軸受メーカーが想定している油浴状態とは異なり、軸受部による油の流れへの抵抗により、軸受部上流側の油面が上昇し、その結果、油と軸受部との接触面積が増大し、油の撹拌ロスが増加する。 In oil-cooled screw compressors, oil agitation loss is an important problem, and among the oil agitation loss, the agitation loss in the bearing portion of the screw rotor is the main factor. The bearing portion of the compressor is cooled and lubricated by oil and has a structure through which oil always passes. In particular, since the bearing portion on the discharge side is usually cooled and lubricated by the oil that seals the shaft seal portion, it is difficult to adjust the amount of oil. Therefore, in the bearing part on the discharge side, unlike the oil bath state assumed by the bearing manufacturer, the oil level on the upstream side of the bearing part rises due to the resistance to the oil flow by the bearing part. The contact area with the bearing portion increases, and the oil agitation loss increases.
　特許文献１には、油冷式スクリュ圧縮機の軸受部の排油構造が開示されている。この油冷式スクリュ圧縮機では、軸受部の外輪抑えスリーブに環状空間を設けることで、油が軸受部下流側の空間に溜まることによる油の撹拌ロスを防止している。 Patent Document 1 discloses an oil discharge structure of a bearing portion of an oil-cooled screw compressor. In this oil-cooled screw compressor, an annular space is provided in the outer ring restraining sleeve of the bearing portion, thereby preventing oil agitation loss due to accumulation of oil in the space on the downstream side of the bearing portion.
特開平１０－２８８１７５号公報Japanese Patent Laid-Open No. 10-288175
　ここで、特許文献１の油冷式スクリュ圧縮機では、軸受部下流側の油の溜まりは考慮されているが、軸受部上流側の油面位置や軸受部を通過する油量については、考慮されていない。 Here, in the oil-cooled screw compressor of Patent Document 1, the oil pool on the downstream side of the bearing portion is considered, but the oil level position on the upstream side of the bearing portion and the amount of oil passing through the bearing portion are considered. It has not been.
　そこで本発明では、軸受部上流側における油の撹拌ロスを低減できる、油冷式スクリュ圧縮機を提供することを目的とする。 Therefore, an object of the present invention is to provide an oil-cooled screw compressor that can reduce oil agitation loss on the upstream side of the bearing portion.
　本発明の一態様は、油冷式スクリュ圧縮機が、噛み合い状態で回転してガスを圧縮する一対のスクリュロータと、
　前記一対のスクリュロータを収容するケーシングと、
　前記スクリュロータの吐出側ロータ軸を支持する吐出側軸受部と、
　前記吐出側ロータ軸を軸封する軸封部と、
　前記軸封部と前記吐出側軸受部との間に設けられる第１空間と、
　前記吐出側軸受部の軸方向端部と前記ケーシングとの間に設けられる第２空間と、
　前記ケーシングに形成され、前記第１空間と前記第２空間とを連通する連絡通路と、を備えていることを特徴とする。 One aspect of the present invention is a pair of screw rotors in which an oil-cooled screw compressor rotates in an engaged state to compress gas,
A casing for accommodating the pair of screw rotors;
A discharge-side bearing portion that supports a discharge-side rotor shaft of the screw rotor;
A shaft seal portion for sealing the discharge-side rotor shaft;
A first space provided between the shaft sealing portion and the discharge-side bearing portion;
A second space provided between an axial end of the discharge side bearing portion and the casing;
A communication passage formed in the casing and communicating with the first space and the second space is provided.
　前記構成によれば、第１空間と第２空間とを連通する連絡通路を備えているので、第１空間である吐出側軸受部上流側の余分な油が第２空間に移動することにより、吐出側軸受部上流側における油の撹拌ロスを低減できる。 According to the above configuration, since the communication passage that communicates the first space and the second space is provided, excess oil on the upstream side of the discharge-side bearing portion that is the first space moves to the second space, Oil agitation loss on the upstream side of the discharge side bearing portion can be reduced.
　前記態様は、さらに、次のような構成を備えるのが好ましい。 It is preferable that the aspect further includes the following configuration.
（１）前記連絡通路の前記吐出側軸受部に接する部分の接触下端は、前記吐出側軸受部の内輪転送面の最下端と、前記吐出側軸受部の外輪転送面の最下端との間に位置している。 (1) The contact lower end of the portion of the communication passage in contact with the discharge side bearing portion is between the lowermost end of the inner ring transfer surface of the discharge side bearing portion and the lower end of the outer ring transfer surface of the discharge side bearing portion. positioned.
　前記構成（１）によれば、連絡通路の吐出側軸受部に接する部分の下端を吐出側軸受部の内輪転送面の最下端と外輪転送面の最下端との間に配置することによって、第１空間の油面位置を転動体が油浴する高さに保持することができ、必要な油量を軸受部に供給しながら、連絡通路によって余分な油を第２空間に移動させることができる。 According to the configuration (1), the lower end of the portion of the communication passage that is in contact with the discharge-side bearing portion is disposed between the lowermost end of the inner ring transfer surface and the lowermost end of the outer ring transfer surface of the discharge-side bearing portion. The oil surface position in one space can be maintained at a height at which the rolling elements bathe, and excess oil can be moved to the second space by the communication passage while supplying the required amount of oil to the bearing portion. .
（２）前記構成（１）において、前記接触下端は、前記吐出側軸受部の転動体の中心の軌道円の最下端と、前記吐出側軸受部の外輪転送面の最下端との間に位置している。 (2) In the configuration (1), the lower end of the contact is located between the lowermost end of the orbital circle at the center of the rolling element of the discharge side bearing portion and the lowermost end of the outer ring transfer surface of the discharge side bearing portion. is doing.
　前記構成（２）によれば、連絡通路の接触下端を吐出側軸受部の転動体の中心の軌道円の最下端と外輪転送面の最下端との間に配置することによって、第１空間の油面位置をより転動体の中心位置から外輪転送面までの間に保持することができ、必要かつより少量の油量を軸受部に供給しながら、連絡通路によって余分な油を第２空間に移動させることができる。 According to the configuration (2), the lower end of the contact of the communication passage is disposed between the lowermost end of the orbital circle at the center of the rolling element of the discharge-side bearing portion and the lowermost end of the outer ring transfer surface. The oil level position can be further maintained between the center position of the rolling elements and the outer ring transfer surface, and excess oil is supplied to the second space by the communication passage while supplying a necessary and smaller amount of oil to the bearing portion. Can be moved.
（３）前記吐出側ロータ軸の軸方向に垂直な断面において、
　前記一対のスクリュロータにより圧縮された圧縮ガスを排出する吐出ポートは、前記吐出側ロータ軸の軸心を結ぶ直線に対して下方又は側方に配置され、
　前記連絡通路は、圧縮ガスによって前記吐出側ロータ軸に作用するガス作用力の方向に垂直な面であって、前記吐出側ロータ軸の軸心を通る、ガス作用力面に対して前記吐出ポート側に設けられている。 (3) In a cross section perpendicular to the axial direction of the discharge-side rotor shaft,
The discharge port for discharging the compressed gas compressed by the pair of screw rotors is disposed below or laterally with respect to a straight line connecting the axis of the discharge side rotor shaft,
The communication passage is a surface perpendicular to the direction of the gas acting force acting on the discharge side rotor shaft by the compressed gas, and passes through the axis of the discharge side rotor shaft, and the discharge port with respect to the gas acting force surface On the side.
　前記構成（３）によれば、吐出側ロータ軸は、圧縮ガスから力を受けるようになっている。ここで、連絡通路を、ガス作用力面に対して吐出ポート側、すなわち、圧縮ガスから受けるガス作用力の方向の反対側に設けることによって、ケーシングによる吐出側軸受部の支持力を低下させることなく、連絡通路を設けることができる。 According to the configuration (3), the discharge-side rotor shaft receives a force from the compressed gas. Here, by providing the communication passage on the discharge port side with respect to the gas action force surface, that is, on the opposite side of the direction of the gas action force received from the compressed gas, the support force of the discharge side bearing portion by the casing is reduced. And a communication passage can be provided.
（４）前記構成（３）において、前記吐出側ロータ軸の軸方向に垂直な断面において、
　前記吐出側ロータ軸の軸心を結ぶ直線と水平線とのなす角度は、０度以上４５度以下であり、
　前記連絡通路は、前記軸心を通り、前記軸心に対して前記ガス作用力と反対の方向に延びる反ガス作用力線に対して下方に４５度の角度をなす第１傾斜線と、前記反ガス作用力線に対して上方に４５度の角度をなす第２傾斜線と、によって挟まれる範囲に設けられている。 (4) In the configuration (3), in a cross section perpendicular to the axial direction of the discharge-side rotor shaft,
An angle formed by a straight line connecting the axis of the discharge-side rotor shaft and a horizontal line is 0 degree or more and 45 degrees or less,
The communication passage passes through the axis and has a first inclined line that forms an angle of 45 degrees downward with respect to an anti-gas action force line extending in a direction opposite to the gas action force with respect to the axis; It is provided in a range sandwiched by a second inclined line that forms an angle of 45 degrees upward with respect to the anti-gas acting force line.
　前記構成（４）によれば、連絡通路を、圧縮ガスから受けるガス作用力の方向の反対側の所定の範囲に設けることによって、ケーシングによる吐出側軸受部の支持力を低下させることなく、連絡通路を設けることができる。 According to the configuration (4), the communication passage is provided in a predetermined range on the opposite side of the direction of the gas acting force received from the compressed gas, so that the communication without reducing the supporting force of the discharge side bearing portion by the casing. A passage can be provided.
（５）前記連絡通路は、直線状に延びており、前記吐出側ロータ軸と平行である長手方向軸を有している。 (5) The communication passage extends in a straight line and has a longitudinal axis parallel to the discharge-side rotor shaft.
　前記構成（５）によれば、連絡通路を機械加工で製作する場合、ケーシングの外部方向から１度の機械加工で製作することができるので、連絡通路の製作性及び製造コストを有利とすることができる。また、連絡通路を鋳物で製作する場合であっても、簡単な構造であるため、鋳型の抜き方向を考慮することなく、軸受保持穴の型の一部を改造するだけで製作が可能であり、連絡通路の製作性及び製造コストを有利とすることができる。 According to the configuration (5), when the connecting passage is manufactured by machining, the connecting passage can be manufactured by one machining from the outside of the casing. Can do. Even when the communication passage is made of cast metal, it has a simple structure, so it can be manufactured by simply modifying a part of the bearing holding hole mold without considering the mold removal direction. Further, the manufacturability and the manufacturing cost of the communication passage can be advantageous.
（６）前記連絡通路を複数備えている。 (6) A plurality of communication passages are provided.
　前記構成（６）によれば、第１空間から第２空間への油の移動量が十分でなく、油面が上昇するような場合でも、連絡通路を複数備えることによって、油面位置が大きく上昇することを防止できる。 According to the configuration (6), even when the amount of movement of oil from the first space to the second space is not sufficient and the oil level rises, the oil level position is increased by providing a plurality of communication passages. It can be prevented from rising.
　本発明の第２態様は、噛み合い状態で回転してガスを圧縮する一対のスクリュロータと、
　前記一対のスクリュロータを収容するケーシングと、
　前記スクリュロータの吸込側ロータ軸を支持する吸込側軸受部と、
　前記吸込側軸受部の軸方向端部と前記ケーシングとの間に設けられる第３空間と、
　前記スクリュロータがガスを吸い込む吸込空間と、
　前記ケーシングに形成され、前記第３空間と前記吸込空間とを連通する第２連絡通路と、を備えていることを特徴とする。 A second aspect of the present invention includes a pair of screw rotors that rotate in an engaged state and compress gas.
A casing for accommodating the pair of screw rotors;
A suction side bearing portion that supports a suction side rotor shaft of the screw rotor;
A third space provided between the axial end of the suction side bearing portion and the casing;
A suction space into which the screw rotor sucks gas;
A second communication passage formed in the casing and communicating the third space and the suction space is provided.
　前記構成によれば、第３空間と吸込空間とを連通する第２連絡通路を備えているので、第３空間である吸込側軸受部上流側の余分な油が吸込空間に移動することにより、吸込側軸受部上流側における油の撹拌ロスを低減できる。 According to the above configuration, since the second communication passage that communicates the third space and the suction space is provided, excess oil on the upstream side of the suction side bearing portion that is the third space moves to the suction space. Oil agitation loss on the upstream side of the suction side bearing portion can be reduced.
　前記第２態様は、さらに、次のような構成を備えるのが好ましい。 The second aspect preferably further comprises the following configuration.
（７）前記第２連絡通路の前記吸込側軸受部に接する部分の接触下端は、前記吸込側軸受部の内輪転送面の最下端と、前記吸込側軸受部の外輪転送面の最下端との間に位置している。 (7) The lower end of the contact portion of the second communication passage that is in contact with the suction side bearing portion is the lowermost end of the inner ring transfer surface of the suction side bearing portion and the lowermost end of the outer ring transfer surface of the suction side bearing portion. Located between.
　前記構成（７）によれば、第２連絡通路の吸込側軸受部に接する部分の下端を吸込側軸受部の内輪転送面の最下端と外輪転送面の最下端との間に配置することによって、第３空間の油面位置を転動体が油浴する高さに保持することができ、必要な油量を軸受部に供給しながら、第２連絡通路によって余分な油を吸込空間に移動させることができる。 According to said structure (7), by arrange | positioning the lower end of the part which contact | connects the suction side bearing part of a 2nd communication path between the lowest end of the inner ring transfer surface of a suction side bearing part, and the lowest end of an outer ring transfer surface. The oil level position of the third space can be maintained at a height at which the rolling elements bathe, and the excess oil is moved to the suction space by the second communication passage while supplying the required amount of oil to the bearing portion. be able to.
（８）前記構成（７）において、前記接触下端は、前記吸込側軸受部の転動体の中心の軌道円の最下端と、前記吸込側軸受部の外輪転送面の最下端との間に位置している。 (8) In the configuration (7), the lower end of the contact is located between the lowermost end of the orbital circle at the center of the rolling element of the suction side bearing portion and the lowermost end of the outer ring transfer surface of the suction side bearing portion. is doing.
　前記構成（８）によれば、第２連絡通路の接触下端を吸込側軸受部の転動体の中心の軌道円の最下端と外輪転送面の最下端との間に配置することによって、第３空間の油面位置をより転動体の中心位置から外輪転送面までの間に保持することができ、必要かつより少量の油量を軸受部に供給しながら、第２連絡通路によって余分な油を吸込空間に移動させることができる。 According to the configuration (8), the contact lower end of the second communication passage is arranged between the lowermost end of the orbital circle at the center of the rolling element of the suction side bearing portion and the lowermost end of the outer ring transfer surface, whereby the third The oil surface position of the space can be maintained between the center position of the rolling elements and the outer ring transfer surface, and excess oil can be removed by the second communication passage while supplying a necessary and smaller amount of oil to the bearing portion. It can be moved to the suction space.
（９）前記吸込側ロータ軸の軸方向に垂直な断面において、
　前記一対のスクリュロータにより圧縮された圧縮ガスを排出する吐出ポートは、前記吸込側ロータ軸の軸心を結ぶ直線に対して下方又は側方に配置され、
　前記第２連絡通路は、圧縮ガスによって前記吸込側ロータ軸に作用するガス作用力の方向に垂直な面であって、前記吸込側ロータ軸の軸心を通る、ガス作用力面に対して前記吐出ポート側に設けられている。 (9) In a cross section perpendicular to the axial direction of the suction side rotor shaft,
The discharge port for discharging the compressed gas compressed by the pair of screw rotors is disposed below or laterally with respect to a straight line connecting the axis of the suction side rotor shaft,
The second communication passage is a surface perpendicular to the direction of the gas acting force acting on the suction side rotor shaft by the compressed gas, and passes through the axial center of the suction side rotor shaft and the gas acting force surface. It is provided on the discharge port side.
　前記構成（９）によれば、吸込側ロータ軸は、圧縮ガスから力を受けるようになっている。ここで、第２連絡通路を、ガス作用力面に対して吐出ポート側、すなわち、圧縮ガスから受けるガス作用力の方向の反対側に設けることによって、ケーシングによる吸込側軸受部の支持力を低下させることなく、第２連絡通路を設けることができる。 According to the configuration (9), the suction-side rotor shaft receives a force from the compressed gas. Here, by providing the second communication passage on the discharge port side with respect to the gas acting force surface, that is, on the opposite side of the direction of the gas acting force received from the compressed gas, the supporting force of the suction side bearing portion by the casing is reduced. Without this, the second communication passage can be provided.
（１０）前記構成（９）において、前記吸込側ロータ軸の軸方向に垂直な断面において、
　前記吸込側ロータ軸の軸心を結ぶ直線と水平線とのなす角度は、０度以上４５度以下であり、
　前記第２連絡通路は、前記軸心を通り、前記軸心に対して前記ガス作用力と反対の方向に延びる反ガス作用力線に対して下方に４５度の角度をなす第１傾斜線と、前記反ガス作用力線に対して上方に４５度の角度をなす第２傾斜線と、によって挟まれる範囲に設けられている。 (10) In the configuration (9), in a cross section perpendicular to the axial direction of the suction side rotor shaft,
An angle formed by a straight line connecting the axis of the suction side rotor shaft and a horizontal line is 0 degree or more and 45 degrees or less,
The second communication passage includes a first inclined line that passes through the axis and forms an angle of 45 degrees downward with respect to an anti-gas action force line extending in a direction opposite to the gas action force with respect to the axis. , And a second inclined line having an angle of 45 degrees upward with respect to the anti-gas acting force line.
　前記構成（１０）によれば、第２連絡通路を、圧縮ガスから受けるガス作用力の方向の反対側の所定の範囲に設けることによって、ケーシングによる吸込側軸受部の支持力を低下させることなく、第２連絡通路を設けることができる。 According to the configuration (10), by providing the second communication passage in a predetermined range opposite to the direction of the gas acting force received from the compressed gas, the supporting force of the suction side bearing portion by the casing is not reduced. A second communication passage can be provided.
（１１）前記第２連絡通路は、直線状に延びており、前記吸込側ロータ軸と平行である長手方向軸を有している。 (11) The second communication passage extends linearly and has a longitudinal axis parallel to the suction-side rotor shaft.
　前記構成（１１）によれば、第２連絡通路を機械加工で製作する場合、ケーシングの外部方向から１度の機械加工で製作することができるので、第２連絡通路の製作性及び製造コストを有利とすることができる。また、第２連絡通路を鋳物で製作する場合であっても、簡単な構造であるため、鋳型の抜き方向を考慮することなく、軸受保持穴の型の一部を改造するだけで製作が可能であり、第２連絡通路の製作性及び製造コストを有利とすることができる。 According to the configuration (11), when the second connecting passage is manufactured by machining, the second connecting passage can be manufactured by one machining from the outside of the casing. Can be advantageous. Even if the second communication passage is made of cast metal, it has a simple structure, so it can be made by simply modifying a part of the bearing holding hole mold without considering the mold removal direction. Thus, the manufacturability and manufacturing cost of the second communication passage can be advantageous.
（１２）前記第２連絡通路を複数備えている。 (12) A plurality of the second communication passages are provided.
　前記構成（１２）によれば、第３空間から吸込空間への油の移動量が十分でなく、油面が上昇するような場合でも、第２連絡通路を複数備えることによって、油面位置が大きく上昇することを防止できる。 According to the configuration (12), even when the amount of movement of oil from the third space to the suction space is not sufficient and the oil level rises, the oil level position is determined by providing a plurality of second communication passages. It is possible to prevent a large rise.
　本発明の第３態様は、噛み合い状態で回転してガスを圧縮する一対のスクリュロータと、
　前記一対のスクリュロータを収容するケーシングと、
　前記スクリュロータの吐出側ロータ軸を支持する吐出側軸受部と、
　前記吐出側ロータ軸を軸封する軸封部と、
　前記軸封部と前記吐出側軸受部との間に設けられる第１空間と、
　前記吐出側軸受部の軸方向端部と前記ケーシングとの間に設けられる第２空間と、
　前記ケーシングに形成され、前記第１空間と前記第２空間とを連通する連絡通路と、
　前記スクリュロータの吸込側ロータ軸を支持する吸込側軸受部と、
　前記吸込側軸受部の軸方向端部と前記ケーシングとの間に設けられる第３空間と、
　前記スクリュロータがガスを吸い込む吸込空間と、
　前記ケーシングに形成され、前記第３空間と前記吸込空間とを連通する第２連絡通路と、を備え、
　前記連絡通路と前記第２連絡通路とは、前記スクリュロータの軸方向から見て重なる位置に設けられていることを特徴とする。 A third aspect of the present invention comprises a pair of screw rotors that rotate in mesh and compress gas.
A casing for accommodating the pair of screw rotors;
A discharge-side bearing portion that supports a discharge-side rotor shaft of the screw rotor;
A shaft seal portion for sealing the discharge-side rotor shaft;
A first space provided between the shaft sealing portion and the discharge-side bearing portion;
A second space provided between an axial end of the discharge side bearing portion and the casing;
A communication passage formed in the casing and communicating between the first space and the second space;
A suction side bearing portion that supports a suction side rotor shaft of the screw rotor;
A third space provided between the axial end of the suction side bearing portion and the casing;
A suction space into which the screw rotor sucks gas;
A second communication passage formed in the casing and communicating with the third space and the suction space;
The communication passage and the second communication passage are provided at positions overlapping each other when viewed from the axial direction of the screw rotor.
　前記構成によれば、連絡通路と第２連絡通路とは、スクリュロータの軸方向から見て重なる位置に設けられているので、ケーシングによる吐出側軸受部及び吸込側軸受部の支持力を両方共低下させることなく、連絡通路及び第２連絡通路を設けることができる。 According to the above configuration, since the communication passage and the second communication passage are provided at positions overlapping each other when viewed from the axial direction of the screw rotor, both the supporting forces of the discharge side bearing portion and the suction side bearing portion by the casing are shared. The communication passage and the second communication passage can be provided without being lowered.
　本発明によると、軸受部上流側における油の撹拌ロスを低減できる、油冷式スクリュ圧縮機を提供できる。 According to the present invention, an oil-cooled screw compressor that can reduce oil agitation loss on the upstream side of the bearing can be provided.
本発明の第１実施形態に係る油冷式スクリュ圧縮機の平面部分断面図。The plane partial sectional view of the oil-cooled screw compressor concerning a 1st embodiment of the present invention. 図１のII－II線に沿った部分断面図。FIG. 2 is a partial sectional view taken along line II-II in FIG. 図１のIII－III線に沿った部分断面図。FIG. 3 is a partial sectional view taken along line III-III in FIG. 1. 図１のIV－IVに沿った部分断面図。FIG. 4 is a partial cross-sectional view along IV-IV in FIG. 1. 本発明の第２実施形態に係るスクリュ圧縮機の吐出側軸受部の部分断面図。The fragmentary sectional view of the discharge side bearing part of the screw compressor concerning a 2nd embodiment of the present invention. 本発明の第３実施形態に係るスクリュ圧縮機の吐出側軸受部の部分断面図。The fragmentary sectional view of the discharge side bearing part of the screw compressor concerning a 3rd embodiment of the present invention. 連絡通路の変形例を示す、スクリュ圧縮機の吐出側軸受部の部分断面図。The fragmentary sectional view of the discharge side bearing part of a screw compressor which shows the modification of a communicating path. 連絡通路の変形例を示す、スクリュ圧縮機の吐出側軸受部の部分断面図。The fragmentary sectional view of the discharge side bearing part of a screw compressor which shows the modification of a communicating path. 吸込側に連絡通路が設けられる場合の油冷式スクリュ圧縮機の平面部分断面図。The plane fragmentary sectional view of an oil-cooled screw compressor in case a connecting passage is provided in the suction side. 図９のX-X線に沿った部分断面図。FIG. 10 is a partial cross-sectional view taken along line XX in FIG. 9.
　以下、添付図面を参照して本発明の実施形態を説明する。 Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
（第１実施形態）
　図１は、本発明の第１実施形態に係る油冷式スクリュ圧縮機２の平面部分断面図である。図２は、図１のII-II線に沿った部分断面図、図３は、図１のIII-III線に沿った部分断面図、図４は図１のIV-IV線に沿った部分断面図である。 (First embodiment)
FIG. 1 is a partial plan view of a plane of an oil-cooled screw compressor 2 according to the first embodiment of the present invention. 2 is a partial cross-sectional view taken along line II-II in FIG. 1, FIG. 3 is a partial cross-sectional view taken along line III-III in FIG. 1, and FIG. 4 is a partial cross-sectional view taken along line IV-IV in FIG. It is sectional drawing.
　図１～図４に示されるように、本実施形態のスクリュ圧縮機２は、鋳物からなるケーシング４が形成する圧縮室６の中に、雌雄一対の互いに噛合する雄ロータ８（スクリュロータ）および雌ロータ９（スクリュロータ）を回転可能に収容している。雄ロータ８は、空気を圧縮する雄ロータ本体８ａと、雄ロータ本体８ａを支持する吸込側ロータ軸８ｂ及び吐出側ロータ軸８ｃとを備える。同様に、雌ロータ９は、雄ロータ本体８ａと噛合して空気を圧縮する雌ロータ本体９ａと、雌ロータ本体９ａを支持する吸込側ロータ軸９ｂ及び吐出側ロータ軸９ｃとを備える。また、吸込空間４８から吸い込まれ、雄ロータ本体８ａと雌ロータ本体９ａにより圧縮された空気は、吐出ポート４９から排出され、吐出口５０を通じて、次の設備等に供給される。 As shown in FIGS. 1 to 4, the screw compressor 2 of this embodiment includes a male and female pair of male rotors 8 (screw rotors) that mesh with each other in a compression chamber 6 formed by a casing 4 made of a casting. A female rotor 9 (screw rotor) is rotatably accommodated. The male rotor 8 includes a male rotor body 8a that compresses air, and a suction-side rotor shaft 8b and a discharge-side rotor shaft 8c that support the male rotor body 8a. Similarly, the female rotor 9 includes a female rotor body 9a that meshes with the male rotor body 8a to compress air, and a suction-side rotor shaft 9b and a discharge-side rotor shaft 9c that support the female rotor body 9a. The air sucked from the suction space 48 and compressed by the male rotor main body 8a and the female rotor main body 9a is discharged from the discharge port 49 and supplied to the next facility or the like through the discharge port 50.
　ケーシング４内には、圧縮室６と共に軸受室１０が形成されている。吐出側ロータ軸８ｃ、９ｃとケーシング４との間には、軸封部（吐出側軸封部）１４が配設されており、圧縮室６と軸受室１０との間を隔離している。 In the casing 4, a bearing chamber 10 is formed together with the compression chamber 6. Between the discharge- side rotor shafts 8 c and 9 c and the casing 4, a shaft seal portion (discharge-side shaft seal portion) 14 is disposed to isolate the compression chamber 6 from the bearing chamber 10.
　軸受室１０には、吐出側ロータ軸８ｃ、９ｃを回転自在に支持する吐出側軸受部１６が収容されている。図４に示されるように、吐出側軸受部１６は、リング状の内輪１８と、リング状の外輪２０と、それらの間に配置された球状または円柱状の転動体２２とを備える。図１及び図２に示されるように、吐出側軸受部１６によって軸受室１０内が、軸受上流空間（第１空間）２４と軸受下流空間（第２空間）２６とに仕切られている。第１空間２４は、軸封部１４、吐出側軸受部１６及びケーシング４によって画定されている。 The bearing chamber 10 accommodates a discharge-side bearing portion 16 that rotatably supports the discharge- side rotor shafts 8c and 9c. As shown in FIG. 4, the discharge-side bearing portion 16 includes a ring-shaped inner ring 18, a ring-shaped outer ring 20, and a spherical or columnar rolling element 22 disposed therebetween. As shown in FIGS. 1 and 2, the inside of the bearing chamber 10 is partitioned into a bearing upstream space (first space) 24 and a bearing downstream space (second space) 26 by the discharge-side bearing portion 16. The first space 24 is defined by the shaft seal portion 14, the discharge side bearing portion 16, and the casing 4.
　図１に示されるように、本実施形態のスクリュ圧縮機２は、雄ロータ８の吸込側ロータ軸８ｂがケーシング４の外側に延伸し、不図示のモータ等に接続されている。従って、雄ロータ８の吸込側ロータ軸８ｂがケーシング４を貫通する部分にも軸封部（図示せず）が設けられている。一方、吐出側ロータ軸８ｃ、９ｃの端部はケーシング４内に収容されている。吐出側ロータ軸８ｃ、９ｃの端部には、スラスト荷重を受け止めるための軸受内輪抑え２８及び軸受外輪抑え３０が設けられている。軸受内輪抑え２８は、吐出側軸受部１６の内輪１８と当接し、軸受外輪抑え３０は、吐出側軸受部１６の外輪２０と当接し、内輪１８及び外輪２０の軸方向の移動をそれぞれ制限している。第２空間２６は、吐出側軸受部１６、ケーシング４及び軸受外輪抑え３０によって画定されている。 As shown in FIG. 1, in the screw compressor 2 of the present embodiment, the suction side rotor shaft 8b of the male rotor 8 extends to the outside of the casing 4 and is connected to a motor or the like (not shown). Accordingly, a shaft sealing portion (not shown) is also provided at a portion where the suction side rotor shaft 8 b of the male rotor 8 passes through the casing 4. On the other hand, end portions of the discharge- side rotor shafts 8 c and 9 c are accommodated in the casing 4. A bearing inner ring restrainer 28 and a bearing outer ring restrainer 30 for receiving a thrust load are provided at the ends of the discharge- side rotor shafts 8c and 9c. The bearing inner ring restraint 28 is in contact with the inner ring 18 of the discharge side bearing portion 16, and the bearing outer ring restraint 30 is in contact with the outer ring 20 of the discharge side bearing portion 16 to restrict axial movement of the inner ring 18 and the outer ring 20. ing. The second space 26 is defined by the discharge-side bearing portion 16, the casing 4, and the bearing outer ring retainer 30.
　図２に示されるように、ケーシング４の下方には、スクリュロータ８、９に油を供給するためのロータ給油口３２が設けられている。ロータ給油口３２は、ケーシング４を貫通して設けられており、雄ロータ本体８ａ及び雌ロータ本体９ａによって空気を閉じ込めて圧縮した後の圧縮室６内の下側（高圧側）部分と連通している。ロータ給油口３２を通じて供給される油によって、圧縮途中の空気を冷却すると共に隙間をシールし、圧縮性能を向上させている。 As shown in FIG. 2, a rotor oil supply port 32 for supplying oil to the screw rotors 8 and 9 is provided below the casing 4. The rotor refueling port 32 is provided through the casing 4 and communicates with a lower (high pressure side) portion in the compression chamber 6 after the air is trapped and compressed by the male rotor main body 8a and the female rotor main body 9a. ing. The oil supplied through the rotor oil supply port 32 cools the air in the middle of compression and seals the gap to improve the compression performance.
　また、ケーシング４には、軸封給油口３４が設けられている。軸封給油口３４は、ロータ給油口３２と同様にケーシング４を貫通して設けられている。軸封給油口３４は、軸封部１４及び吐出側軸受部１６に油を供給するため、軸封部１４と吐出側軸受部１６との間に設けられる第１空間２４と連通している。軸封給油口３４を通じて軸封部１４に油が供給されることで、圧縮空気を軸封部１４でシールし、圧縮空気が軸封部１４から漏れ出すことを抑止している。また、軸封給油口３４を通じて吐出側軸受部１６に油が供給されることで吐出側軸受部１６を冷却すると共に潤滑し、軸受の損傷を防止している。 Further, the casing 4 is provided with a shaft seal oil supply port 34. The shaft seal oil filler 34 is provided through the casing 4 in the same manner as the rotor oil filler 32. The shaft seal oil supply port 34 communicates with a first space 24 provided between the shaft seal portion 14 and the discharge side bearing portion 16 in order to supply oil to the shaft seal portion 14 and the discharge side bearing portion 16. By supplying oil to the shaft seal portion 14 through the shaft seal oil supply port 34, the compressed air is sealed by the shaft seal portion 14, and the compressed air is prevented from leaking from the shaft seal portion 14. Further, oil is supplied to the discharge-side bearing portion 16 through the shaft seal oil supply port 34, whereby the discharge-side bearing portion 16 is cooled and lubricated to prevent damage to the bearing.
　図１及び図２に示されるように、本実施形態のスクリュ圧縮機２は、第１空間２４に溜まった油を排油するため、第１空間２４と、吐出側軸受部１６の軸方向端部とケーシング４及び軸受外輪抑え３０との間に設けられる第２空間２６とを連通する連絡通路４４ａ、４４ｂを備えている。連絡通路４４ａ、４４ｂは、ケーシング４に切欠きを設けることによって形成されており、それぞれ、直線状に延びており、吐出側ロータ軸８ｃ、９ｃと平行である長手方向軸を有している。なお、連絡通路４４ａ、４４ｂが第１空間２４と第２空間２６とを連通するために、軸受外輪抑え３０にも切欠き３０ａが形成されている。吐出側ロータ軸８ｃ、９ｃの軸方向に垂直な断面において、連絡通路４４ａ、４４ｂは円弧形状を有している。 As shown in FIGS. 1 and 2, the screw compressor 2 of the present embodiment drains the oil accumulated in the first space 24, and therefore the first space 24 and the axial end of the discharge-side bearing portion 16. And communication passages 44 a and 44 b communicating with the second space 26 provided between the portion and the casing 4 and the bearing outer ring retainer 30. The communication passages 44a and 44b are formed by providing a cutout in the casing 4, each extending linearly and having a longitudinal axis parallel to the discharge- side rotor shafts 8c and 9c. Note that a notch 30 a is also formed in the bearing outer ring retainer 30 so that the communication passages 44 a and 44 b communicate the first space 24 and the second space 26. In the cross section perpendicular to the axial direction of the discharge- side rotor shafts 8c, 9c, the communication passages 44a, 44b have an arc shape.
　図４に示されるように、連絡通路４４ａ、４４ｂの吐出側軸受部１６に接する部分の接触下端４４ａ１、４４ｂ１は、上下方向において、吐出側軸受部１６の内輪１８の内輪転送面の最下端１８ａと、吐出側軸受部１６の外輪２０の外輪転送面の最下端２０ａとの間に位置している。さらに詳細には、接触下端４４ａ１、４４ｂ１は、吐出側軸受部１６の転動体２２の中心の軌道円２２ａの最下端２２ａ１と、吐出側軸受部１６の外輪転送面の最下端２０ａとの間に位置している。 As shown in FIG. 4, the contact lower ends 44a1 and 44b1 of the portions of the communication passages 44a and 44b that are in contact with the discharge-side bearing portion 16 have the lowermost end 18a of the inner ring transfer surface of the inner ring 18 of the discharge-side bearing portion 16 in the vertical direction. And the lowermost end 20a of the outer ring transfer surface of the outer ring 20 of the discharge side bearing portion 16. More specifically, the contact lower ends 44a1 and 44b1 are located between the lowermost end 22a1 of the orbital circle 22a at the center of the rolling element 22 of the discharge side bearing portion 16 and the lowermost end 20a of the outer ring transfer surface of the discharge side bearing portion 16. positioned.
　吐出側ロータ軸８ｃ、９ｃは、圧縮ガスから受ける力によって、お互いに離れる方向に力が働く。この力、すなわちガス作用力は、吐出側軸受部１６で受け、吐出側軸受部１６は、ケーシング４で保持されるようになっている。 The discharge- side rotor shafts 8c and 9c act in directions away from each other due to the force received from the compressed gas. This force, that is, the gas acting force is received by the discharge side bearing portion 16, and the discharge side bearing portion 16 is held by the casing 4.
　吐出側ロータ軸８ｃ、９ｃは、水平方向に並んで配置される。本実施形態では、水平線Ｓに対し、吐出側ロータ軸８ｃ、９ｃの軸心８ｃ１、９ｃ１を結ぶ線が０度の角度をなしている。本実施形態では、吐出側ロータ軸８ｃ、９ｃの軸心８ｃ１、９ｃ１を結ぶ線よりも下側に吐出ポート４９が存在している。この場合、吐出側ロータ軸８ｃ側のガス作用力Ｆ１は、吐出側ロータ軸８ｃの軸心８ｃ１と吐出側ロータ軸９ｃの軸心９ｃ１とを通る軸中心線Ｌ１上であって、軸心８ｃ１を通って軸心９ｃ１に対して反対側に延びる線Ｌ１ａに対して、圧縮ガス吐出方向（鉛直下方）とは反対方向へ角度θ１だけ傾斜した方向を向いている。ここで、角度θ１は、６０度程度である。 The discharge- side rotor shafts 8c and 9c are arranged side by side in the horizontal direction. In the present embodiment, the line connecting the shaft centers 8c1 and 9c1 of the discharge- side rotor shafts 8c and 9c makes an angle of 0 degrees with respect to the horizontal line S. In this embodiment, the discharge port 49 exists below the line connecting the shaft centers 8c1 and 9c1 of the discharge- side rotor shafts 8c and 9c. In this case, the gas acting force F1 on the discharge-side rotor shaft 8c side is on an axis center line L1 passing through the shaft center 8c1 of the discharge-side rotor shaft 8c and the shaft center 9c1 of the discharge-side rotor shaft 9c, and the shaft center 8c1. A line L1a extending through the axis 9c1 on the opposite side is directed in a direction inclined by an angle θ1 in a direction opposite to the compressed gas discharge direction (vertically downward). Here, the angle θ1 is about 60 degrees.
　同様に、吐出側ロータ軸９ｃ側のガス作用力Ｆ２は、軸中心線Ｌ１上であって、軸心９ｃ１を通って軸心８ｃ１に対して反対側に延びる線Ｌ１ｂに対して、圧縮ガス吐出方向（鉛直下方）とは反対方向へ角度θ２だけ傾斜した方向を向いている。ここで、角度θ２は、６０度程度である。 Similarly, the gas acting force F2 on the discharge-side rotor shaft 9c side is compressed gas discharge with respect to a line L1b extending on the shaft center line L1 and passing through the shaft center 9c1 on the opposite side to the shaft center 8c1. The direction (vertically below) is directed in a direction inclined by an angle θ2 in the opposite direction. Here, the angle θ2 is about 60 degrees.
　連絡通路４４ａは、ガス作用力Ｆ１の方向に垂直な面であって、軸心８ｃ１を通る、ガス作用力面Ｓ１の下方であり、ガス作用力Ｆ１の方向と反対方向（吐出ポート４９側）に設けられている。 The communication passage 44a is a surface perpendicular to the direction of the gas action force F1, is below the gas action force surface S1 passing through the axis 8c1, and is opposite to the direction of the gas action force F1 (on the discharge port 49 side). Is provided.
　より詳細には、連絡通路４４ａは、軸心８ｃ１を通り、反ガス作用力線Ｆ１’に対して下方に４５度の角度をなす第１傾斜線Ｆ１’ａと、反ガス作用力線Ｆ１’に対して上方に４５度の角度をなす第２傾斜線Ｆ１’ｂと、によって挟まれる範囲に設けられている。なおここで、軸心８ｃ１を通り、ガス作用力Ｆ１と軸心８ｃ１に対して反対の方向に延びる反ガス作用力線を反ガス作用力線Ｆ１’とする。 More specifically, the communication passage 44a passes through the axis 8c1 and forms a first inclined line F1′a and an antigas action force line F1 ′ that form an angle of 45 degrees downward with respect to the antigas action force line F1 ′. Is provided in a range sandwiched between the second inclined line F1′b and an angle of 45 degrees upward. Here, an anti-gas action force line F1 'passing through the axis 8c1 and extending in the opposite direction to the gas action force F1 and the axis 8c1 is referred to as an anti-gas action force line F1'.
　連絡通路４４ｂは、ガス作用力Ｆ２の方向に垂直な面であって、軸心９ｃ２を通る、ガス作用力面Ｓ２の下方であり、ガス作用力Ｆ２の方向と反対方向（吐出ポート４９側）に設けられている。 The communication passage 44b is a surface perpendicular to the direction of the gas action force F2, is below the gas action force surface S2 passing through the axis 9c2, and is opposite to the direction of the gas action force F2 (on the discharge port 49 side). Is provided.
　より詳細には、連絡通路４４ｂは、軸心９ｃ１を通り、反ガス作用力線Ｆ２’に対して下方に４５度の角度をなす第１傾斜線Ｆ２’ａと、反ガス作用力線Ｆ２’に対して上方に４５度の角度をなす第２傾斜線Ｆ２’ｂと、によって挟まれる範囲に設けられている。なおここで、軸心９ｃ１を通り、ガス作用力Ｆ２と軸心９ｃ１に対して反対の方向に延びる反ガス作用力線を反ガス作用力線Ｆ２’とする。 More specifically, the communication passage 44b passes through the axis 9c1 and forms a first inclined line F2′a and an antigas action force line F2 ′ that form an angle of 45 degrees downward with respect to the antigas action force line F2 ′. Is provided in a range sandwiched between the second inclined line F2′b and an angle of 45 degrees upward. Here, an anti-gas action force line F2 'passing through the axis 9c1 and extending in the opposite direction to the gas action force F2 and the axis 9c1 is referred to as an anti-gas action force line F2'.
　さらに、図１及び図２に破線で示されるように、本実施形態のスクリュ圧縮機２は、第２空間２６に溜まった油を排油するため、一端が第２空間２６に連通した排油通路４６を備えている。排油通路４６の他端は、圧縮室６の雄ロータ本体８ａと雌ロータ本体９ａの閉じ込み後の歯溝部８ｅ（雌ロータ本体９ａの歯溝部は図示されていない）に連通しており、第２空間２６から排油された油は、雄ロータ本体８ａと雌ロータ本体９ａの歯溝部８ｅに供給される。 Further, as shown by the broken lines in FIGS. 1 and 2, the screw compressor 2 of the present embodiment drains the oil accumulated in the second space 26, so that one end of the screw compressor communicates with the second space 26. A passage 46 is provided. The other end of the oil discharge passage 46 communicates with the tooth groove portion 8e after the male rotor body 8a and the female rotor body 9a of the compression chamber 6 are closed (the tooth groove portion of the female rotor body 9a is not shown). The oil discharged from the second space 26 is supplied to the tooth groove portions 8e of the male rotor main body 8a and the female rotor main body 9a.
　さらに図２に示されるように、排油通路４６の排油先は、ロータ給油口３２よりも雄ロータ本体８ａと雌ロータ本体９ａの吸込端面８ｆ、９ｆ側（図において右側）に設けられている。吸込端面８ｆ、９ｆとは、雄ロータ本体８ａと雌ロータ本体９ａの吸込側に設けられた端面である。雄ロータ本体８ａ及び雌ロータ本体９ａは、吸込端面８ｆ、９ｆにおいて、吸込側ロータ軸８ｂ、９ｂとそれぞれ接続されている。 Further, as shown in FIG. 2, the oil discharge destination of the oil discharge passage 46 is provided closer to the suction end surfaces 8 f and 9 f (right side in the drawing) of the male rotor main body 8 a and the female rotor main body 9 a than the rotor oil supply port 32. Yes. The suction end faces 8f and 9f are end faces provided on the suction side of the male rotor main body 8a and the female rotor main body 9a. The male rotor body 8a and the female rotor body 9a are connected to the suction side rotor shafts 8b and 9b at the suction end faces 8f and 9f, respectively.
　前記構成のスクリュ圧縮機２によれば、次のような効果を発揮できる。 According to the screw compressor 2 configured as described above, the following effects can be exhibited.
（１）第１空間２４と第２空間２６とを連通する連絡通路４４ａ、４４ｂを備えているので、第１空間２４である吐出側軸受部上流側の余分な油が第２空間２６に移動することにより、吐出側軸受部上流側における油の撹拌ロスを低減できる。 (1) Since the communication passages 44 a and 44 b communicating the first space 24 and the second space 26 are provided, excess oil on the upstream side of the discharge side bearing portion that is the first space 24 moves to the second space 26. By doing so, it is possible to reduce oil agitation loss on the upstream side of the discharge-side bearing portion.
（２）連絡通路４４ａ、４４ｂの吐出側軸受部１６に接する部分の接触下端４４ａ１、４４ｂ１を吐出側軸受部１６の内輪転送面の最下端１８ａと外輪転送面の最下端２０ａとの間に配置することによって、第１空間２４の油面位置を転動体２２が油浴する高さに保持することができ、必要な油量を吐出側軸受部１６に供給しながら、連絡通路４４ａ、４４ｂによって余分な油を第２空間２６に移動させることができる。 (2) The contact lower ends 44a1 and 44b1 of the communication passages 44a and 44b that are in contact with the discharge-side bearing portion 16 are disposed between the lowermost end 18a of the inner ring transfer surface of the discharge-side bearing portion 16 and the lowermost end 20a of the outer ring transfer surface. By doing so, the oil surface position of the first space 24 can be maintained at a height at which the rolling element 22 bathes the oil, and the communication passages 44a and 44b can supply the required amount of oil to the discharge-side bearing portion 16. Excess oil can be moved to the second space 26.
（３）連絡通路４４ａ、４４ｂの接触下端４４ａ１、４４ｂ１を吐出側軸受部１６の転動体２２の中心の軌道円の最下端２２ａ１と外輪転送面の最下端２０ａとの間に配置することによって、第１空間２４の油面位置を転動体２２の中心位置から外輪転送面までの間に保持することができ、必要かつより少量の油量を吐出側軸受部１６に供給しながら、連絡通路４４によって余分な油を第２空間２６に移動させることができる。 (3) By arranging the contact lower ends 44a1 and 44b1 of the communication passages 44a and 44b between the lowermost end 22a1 of the orbital circle at the center of the rolling element 22 of the discharge side bearing portion 16 and the lowermost end 20a of the outer ring transfer surface, The oil surface position of the first space 24 can be held between the center position of the rolling elements 22 and the outer ring transfer surface, and the communication passage 44 is supplied while supplying a necessary and smaller amount of oil to the discharge-side bearing portion 16. Thus, excess oil can be moved to the second space 26.
（４）吐出側ロータ軸８ｃ、９ｃは、圧縮ガスから力を受けるようになっている。ここで、連絡通路４４ａ、４４ｂを、ガス作用力面Ｓ１、Ｓ２の下方、すなわち、圧縮ガスから受けるガス作用力Ｆ１、Ｆ２の方向の反対側（吐出ポート４９側）に設けることによって、ケーシング４による吐出側軸受部１６の支持力を低下させることなく、連絡通路４４ａ、４４ｂを設けることができる。 (4) The discharge- side rotor shafts 8c and 9c receive a force from the compressed gas. Here, by providing the communication passages 44a and 44b below the gas acting force surfaces S1 and S2, that is, on the side opposite to the direction of the gas acting forces F1 and F2 received from the compressed gas (on the discharge port 49 side), the casing 4 The communication passages 44a and 44b can be provided without reducing the supporting force of the discharge-side bearing portion 16 due to the above.
（５）連絡通路４４ａ、４４ｂは、圧縮ガスから受けるガス作用力Ｆ１、Ｆ２の方向の反対側の所定の範囲、すなわち、軸心８ｃ１、９ｃ１を通り、反ガス作用力線Ｆ１’、Ｆ２’に対して下方に４５度の角度をなす第１傾斜線Ｆ１’ａ、Ｆ２’ａと、反ガス作用力線Ｆ１’、Ｆ２’に対して上方に４５度の角度をなす第２傾斜線Ｆ１’ｂ、Ｆ２’ｂと、によって挟まれる範囲に設けられている。連絡通路４４ａ、４４ｂをこの範囲に設けることによって、ケーシング４による吐出側軸受部１６の支持力を低下させることなく、連絡通路４４ａ、４４ｂを設けることができる。 (5) The communication passages 44a and 44b pass through a predetermined range opposite to the direction of the gas acting forces F1 and F2 received from the compressed gas, that is, the shaft centers 8c1 and 9c1, and the antigas acting force lines F1 ′ and F2 ′. The first inclined lines F1′a and F2′a that form an angle of 45 ° downward with respect to the second and the second inclined lines F1 that form an angle of 45 ° with respect to the anti-gas acting force lines F1 ′ and F2 ′. It is provided in a range sandwiched between 'b and F2'b. By providing the communication passages 44a and 44b in this range, the communication passages 44a and 44b can be provided without reducing the supporting force of the discharge side bearing portion 16 by the casing 4.
（６）連絡通路４４ａ、４４ｂは、直線状に延びており、吐出側ロータ軸８ｃ、９ｃと平行である長手方向軸を有している。連絡通路４４ａ、４４ｂを機械加工で製作する場合、ケーシング４の外部方向から１度の機械加工で製作することができるので、連絡通路４４ａ、４４ｂの製作性及び製造コストを有利とすることができる。また、連絡通路４４ａ、４４ｂを鋳物で製作する場合であっても、簡単な構造であるため、鋳型の抜き方向を考慮することなく、軸受保持穴の型の一部を改造するだけで製作が可能であり、連絡通路４４ａ、４４ｂの製作性及び製造コストを有利とすることができる。 (6) The communication passages 44a and 44b extend linearly and have a longitudinal axis parallel to the discharge- side rotor shafts 8c and 9c. When the connecting passages 44a and 44b are manufactured by machining, the connecting passages 44a and 44b can be manufactured by a single machining from the outside of the casing 4, so that the manufacturability and manufacturing cost of the connecting passages 44a and 44b can be advantageous. . Even if the communication passages 44a and 44b are made of cast metal, since the structure is simple, it is possible to manufacture by simply remodeling a part of the bearing holding hole mold without considering the mold drawing direction. It is possible, and the manufacturability and manufacturing cost of the communication passages 44a and 44b can be advantageous.
（７）ロータ給油口３２よりも吸込端面８ｆ、９ｆ側の圧縮室６は、軸受室１０より圧力が低いため、ロータ給油口３２よりも吸込端面８ｆ、９ｆ側に排油先を設けることで、排油通路４６において高圧から低圧への流れが形成され、排油不良を防止できる。換言すると、仮に排油先がロータ給油口３２の位置より吐出端面８ｄ、９ｄ側の場合、排油先の圧力が高くなり排油が困難になる。従って、本構成によって、第２空間２６からの排油が困難となることを防止している。 (7) Since the compression chamber 6 on the suction end surfaces 8f, 9f side is lower than the bearing chamber 10 than the rotor oil supply port 32, the oil discharge destination is provided on the suction end surfaces 8f, 9f side than the rotor oil supply port 32. In the oil discharge passage 46, a flow from high pressure to low pressure is formed, and oil discharge failure can be prevented. In other words, if the oil discharge destination is on the discharge end face 8d, 9d side from the position of the rotor oil supply port 32, the pressure of the oil discharge destination becomes high and oil discharge becomes difficult. Therefore, this configuration prevents oil from being discharged from the second space 26 from becoming difficult.
（第２実施形態）
　図５は、本発明の第２実施形態に係るスクリュ圧縮機２の吐出側軸受部１６の部分断面図である。本実施形態のスクリュ圧縮機２は、吐出側ロータ軸８ｃ、９ｃが上下方向に並んで配置されている。すなわち、本実施形態では、水平線に対して、吐出側ロータ軸８ｃ、９ｃの軸心８ｃ１、９ｃ１を結ぶ線が９０度の角度をなしている。したがって、本実施形態は、吐出側ロータ軸８ｃ、９ｃが水平方向に並んで配置される第１実施形態と、吐出側ロータ軸８ｃ、９ｃの並び方の点で異なっており、それ以外の部分の構成は、第１実施形態と実質的に同様である。 (Second Embodiment)
FIG. 5 is a partial cross-sectional view of the discharge-side bearing portion 16 of the screw compressor 2 according to the second embodiment of the present invention. In the screw compressor 2 of this embodiment, the discharge- side rotor shafts 8c and 9c are arranged side by side in the vertical direction. That is, in the present embodiment, a line connecting the shaft centers 8c1 and 9c1 of the discharge- side rotor shafts 8c and 9c forms an angle of 90 degrees with respect to the horizontal line. Therefore, the present embodiment is different from the first embodiment in which the discharge- side rotor shafts 8c and 9c are arranged side by side in the horizontal direction, and the arrangement of the discharge- side rotor shafts 8c and 9c. The configuration is substantially the same as in the first embodiment.
　図５に示されるように、連絡通路４４ａ、４４ｂの吐出側軸受部１６に接する部分の接触下端４４ａ１、４４ｂ１は、上下方向において、吐出側軸受部１６の内輪１８の内輪転送面の最下端１８ａと、吐出側軸受部１６の外輪２０の外輪転送面の最下端２０ａとの間に位置している。 As shown in FIG. 5, the contact lower ends 44a1 and 44b1 of the portions of the communication passages 44a and 44b that are in contact with the discharge-side bearing portion 16 have the lowermost end 18a of the inner ring transfer surface of the inner ring 18 of the discharge-side bearing portion 16 in the vertical direction. And the lowermost end 20a of the outer ring transfer surface of the outer ring 20 of the discharge side bearing portion 16.
　より詳細には、接触下端４４ａ１、４４ｂ１は、吐出側軸受部１６の転動体２２の中心の軌道円２２ａの最下端２２ａ１と、吐出側軸受部１６の外輪転送面の最下端２０ａとの間に位置している。 More specifically, the contact lower ends 44a1 and 44b1 are located between the lowermost end 22a1 of the orbital circle 22a at the center of the rolling element 22 of the discharge side bearing portion 16 and the lowermost end 20a of the outer ring transfer surface of the discharge side bearing portion 16. positioned.
　吐出側ロータ軸８ｃ、９ｃは、圧縮ガスから受ける力によって、お互いに離れる方向に力が働く。この力、すなわちガス作用力Ｆ１、Ｆ２は、吐出側軸受部１６で受け、吐出側軸受部１６は、ケーシング４で保持されるようになっている。 The discharge- side rotor shafts 8c and 9c act in directions away from each other due to the force received from the compressed gas. This force, that is, the gas acting forces F <b> 1 and F <b> 2 are received by the discharge side bearing portion 16, and the discharge side bearing portion 16 is held by the casing 4.
　吐出側ロータ軸８ｃ、９ｃが上下方向に並んで配置される本実施形態では、吐出側ロータ軸８ｃ、９ｃの軸心８ｃ１、９ｃ１を結ぶ線よりも右側に吐出ポート４９が存在している。この場合、吐出側ロータ軸８ｃ側のガス作用力Ｆ１は、吐出側ロータ軸８ｃの軸心８ｃ１と吐出側ロータ軸９ｃの軸心９ｃ１とを通る軸中心線Ｌ１上であって、軸心８ｃ１を通って軸心９ｃ１に対して反対側に延びる線Ｌ１ａに対して、圧縮ガス吐出方向（右方）とは反対方向へ角度θ３だけ傾斜した方向を向いている。ここで、角度θ３は、６０度程度である。 In the present embodiment in which the discharge- side rotor shafts 8c and 9c are arranged side by side in the vertical direction, the discharge port 49 exists on the right side of the line connecting the shaft centers 8c1 and 9c1 of the discharge- side rotor shafts 8c and 9c. In this case, the gas acting force F1 on the discharge-side rotor shaft 8c side is on an axis center line L1 passing through the shaft center 8c1 of the discharge-side rotor shaft 8c and the shaft center 9c1 of the discharge-side rotor shaft 9c, and the shaft center 8c1. The line L1a extending through the axis 9c1 on the opposite side passes through the direction inclined by the angle θ3 in the direction opposite to the compressed gas discharge direction (rightward). Here, the angle θ3 is about 60 degrees.
　同様に、吐出側ロータ軸９ｃ側のガス作用力Ｆ２は、軸中心線Ｌ１上であって、軸心９ｃ１を通って軸心８ｃ１に対して反対側に延びる線Ｌ１ｂに対して、圧縮ガス吐出方向（右方）とは反対方向へ角度θ４だけ傾斜した方向を向いている。ここで、角度θ４は、６０度程度である。 Similarly, the gas acting force F2 on the discharge-side rotor shaft 9c side is compressed gas discharge with respect to a line L1b extending on the shaft center line L1 and passing through the shaft center 9c1 on the opposite side to the shaft center 8c1. It is directed in a direction inclined by an angle θ4 in a direction opposite to the direction (right side). Here, the angle θ4 is about 60 degrees.
　連絡通路４４ａは、ガス作用力Ｆ１の方向に垂直な面であって、軸心８ｃ１を通る、ガス作用力面Ｓ１のガス作用力Ｆ１の方向と反対方向（右方であり、吐出ポート４９側）に設けられている。 The communication passage 44a is a surface perpendicular to the direction of the gas acting force F1 and passes through the axis 8c1 and is opposite to the direction of the gas acting force F1 of the gas acting force surface S1 (on the right side, on the discharge port 49 side). ).
　連絡通路４４ｂは、ガス作用力Ｆ２の方向に垂直な面であって、軸心９ｃ１を通る、ガス作用力面Ｓ２のガス作用力Ｆ２の方向と反対方向（右方であり、吐出ポート４９側）に設けられている。 The communication passage 44b is a surface perpendicular to the direction of the gas acting force F2, and passes through the shaft center 9c1 and is opposite to the direction of the gas acting force F2 of the gas acting force surface S2 (on the right side, the discharge port 49 side). ).
　吐出側ロータ軸８ｃ、９ｃは、圧縮ガスから力を受けるようになっている。ここで、吐出側ロータ軸８ｃ、９ｃが上下方向に並んで配置されている場合でも、連絡通路４４ａ、４４ｂを、圧縮ガスから受けるガス作用力Ｆ１、Ｆ２の方向の反対側に設けることによって、ケーシング４による吐出側軸受部１６の支持力を低下させることなく、連絡通路４４ａ、４４ｂを設けることができる。 The discharge- side rotor shafts 8c and 9c are adapted to receive a force from the compressed gas. Here, even when the discharge- side rotor shafts 8c and 9c are arranged side by side in the vertical direction, by providing the communication passages 44a and 44b on the opposite side of the direction of the gas acting forces F1 and F2 received from the compressed gas, The communication passages 44a and 44b can be provided without reducing the supporting force of the discharge-side bearing portion 16 by the casing 4.
（第３実施形態）
　図６は、本発明の第３実施形態に係るスクリュ圧縮機２の吐出側軸受部１６の部分断面図である。本実施形態のスクリュ圧縮機２は、吐出側ロータ軸８ｃ、９ｃが上下方向に斜めに並んで配置されている。すなわち、本実施形態では、水平線Ｓに対して、吐出側ロータ軸８ｃ、９ｃの軸心８ｃ１、９ｃ１を結ぶ線が４５度の角度をなしている。したがって、本実施形態は、吐出側ロータ軸８ｃ、９ｃが水平方向に並んで配置される第１実施形態及び吐出側ロータ軸８ｃ、９ｃが上下方向に並んで配置される第２実施形態と、吐出側ロータ軸の並び方の点で異なっており、それ以外の部分の構成は、第１実施解体と実質的に同様である。 (Third embodiment)
FIG. 6 is a partial cross-sectional view of the discharge-side bearing portion 16 of the screw compressor 2 according to the third embodiment of the present invention. In the screw compressor 2 of this embodiment, the discharge- side rotor shafts 8c and 9c are arranged obliquely in the vertical direction. That is, in the present embodiment, the line connecting the shaft centers 8c1 and 9c1 of the discharge- side rotor shafts 8c and 9c makes an angle of 45 degrees with respect to the horizontal line S. Therefore, this embodiment includes the first embodiment in which the discharge- side rotor shafts 8c and 9c are arranged in a horizontal direction and the second embodiment in which the discharge- side rotor shafts 8c and 9c are arranged in a vertical direction, The arrangement differs in the way of arranging the discharge-side rotor shafts, and the configuration of the other parts is substantially the same as in the first embodiment disassembly.
　図６に示されるように、連絡通路４４ａ、４４ｂの吐出側軸受部１６に接する部分の接触下端４４ａ１、４４ｂ１は、上下方向において、吐出側軸受部１６の内輪１８の内輪転送面の最下端１８ａと、吐出側軸受部１６の外輪２０の外輪転送面の最下端２０ａとの間に位置している。 As shown in FIG. 6, the contact lower ends 44a1 and 44b1 of the portions of the communication passages 44a and 44b that are in contact with the discharge-side bearing portion 16 have the lowermost end 18a of the inner ring transfer surface of the inner ring 18 of the discharge-side bearing portion 16 in the vertical direction. And the lowermost end 20a of the outer ring transfer surface of the outer ring 20 of the discharge side bearing portion 16.
　より詳細には、接触下端４４ａ１、４４ｂ１は、吐出側軸受部１６の転動体２２の中心の軌道円２２ａの最下端２２ａ１と、吐出側軸受部１６の外輪転送面の最下端２０ａとの間に位置している。 More specifically, the contact lower ends 44a1 and 44b1 are located between the lowermost end 22a1 of the orbital circle 22a at the center of the rolling element 22 of the discharge side bearing portion 16 and the lowermost end 20a of the outer ring transfer surface of the discharge side bearing portion 16. positioned.
　吐出側ロータ軸８ｃ、９ｃは、圧縮ガスから受ける力によって、お互いに離れる方向に力が働く。この力、すなわちガス作用力Ｆ１、Ｆ２は、吐出側軸受部１６で受け、吐出側軸受部１６は、ケーシング４で保持されるようになっている。 The discharge- side rotor shafts 8c and 9c act in directions away from each other due to the force received from the compressed gas. This force, that is, the gas acting forces F <b> 1 and F <b> 2 are received by the discharge side bearing portion 16, and the discharge side bearing portion 16 is held by the casing 4.
　吐出側ロータ軸８ｃ、９ｃが上下方向斜めに並んで配置される本実施形態では、吐出側ロータ軸８ｃ、９ｃの軸心８ｃ１、９ｃ１を結ぶ線よりも右下側に吐出ポート４９が存在している。この場合、吐出側ロータ軸８ｃ側のガス作用力Ｆ１は、吐出側ロータ軸８ｃの軸心８ｃ１と吐出側ロータ軸９ｃの軸心９ｃ１とを通る軸中心線Ｌ１上であって、軸心８ｃ１を通って軸心９ｃ１に対して反対側に延びる線Ｌ１ａに対して、圧縮ガス吐出方向（右下方）とは反対方向へ角度θ５だけ傾斜した方向を向いている。ここで、角度θ５は、６０度程度である。 In the present embodiment in which the discharge- side rotor shafts 8c and 9c are arranged obliquely in the vertical direction, the discharge port 49 exists on the lower right side of the line connecting the shaft centers 8c1 and 9c1 of the discharge- side rotor shafts 8c and 9c. ing. In this case, the gas acting force F1 on the discharge-side rotor shaft 8c side is on an axis center line L1 passing through the shaft center 8c1 of the discharge-side rotor shaft 8c and the shaft center 9c1 of the discharge-side rotor shaft 9c, and the shaft center 8c1. The line L1a that passes through the axis 9c1 on the opposite side passes through the direction inclined by the angle θ5 in the direction opposite to the compressed gas discharge direction (lower right). Here, the angle θ5 is about 60 degrees.
　同様に、吐出側ロータ軸９ｃ側のガス作用力Ｆ２は、軸中心線Ｌ１上であって、軸心９ｃ１を通って軸心８ｃ１に対して反対側に延びる線Ｌ１ｂに対して、圧縮ガス吐出方向（右下方）とは反対方向へ角度θ６だけ傾斜した方向を向いている。ここで、角度θ６は、６０度程度である。 Similarly, the gas acting force F2 on the discharge-side rotor shaft 9c side is compressed gas discharge with respect to a line L1b extending on the shaft center line L1 and passing through the shaft center 9c1 on the opposite side to the shaft center 8c1. It faces the direction inclined by an angle θ6 in the opposite direction to the direction (lower right). Here, the angle θ6 is about 60 degrees.
　連絡通路４４ａは、ガス作用力Ｆ１の方向に垂直な面であって、軸心８ｃ１を通る、ガス作用力面Ｓ１の右下方であり、ガス作用力Ｆ１の方向と反対方向（吐出ポート４９側）に設けられている。 The communication passage 44a is a surface perpendicular to the direction of the gas acting force F1 and is located on the lower right side of the gas acting force surface S1 passing through the axis 8c1 and in the direction opposite to the direction of the gas acting force F1 (on the discharge port 49 side ).
　より詳細には、連絡通路４４ａは、軸心８ｃ１を通り、反ガス作用力線Ｆ１’に対して下方に４５度の角度をなす第１傾斜線Ｌ５ａと、反ガス作用力線Ｆ１’に対して上方に４５度の角度をなす第２傾斜線Ｌ５ｂと、によって挟まれる範囲に設けられている。なおここで、軸心８ｃ１を通り、ガス作用力Ｆ１と軸心８ｃ１に対して反対の方向に延びる反ガス作用力線を反ガス作用力線Ｆ１’とする。 More specifically, the communication passage 44a passes through the axial center 8c1 and is inclined with respect to the first inclined line L5a and the anti-gas action force line F1 ′ that form an angle of 45 degrees downward with respect to the anti-gas action force line F1 ′. And a second slope line L5b that forms an angle of 45 degrees upward. Here, an anti-gas action force line F1 'passing through the axis 8c1 and extending in the opposite direction to the gas action force F1 and the axis 8c1 is referred to as an anti-gas action force line F1'.
　連絡通路４４ｂは、ガス作用力Ｆ２の方向に垂直な面であって、軸心９ｃ２を通る、ガス作用力面Ｓ２の下方であり、ガス作用力Ｆ２の方向と反対方向（吐出ポート４９側）に設けられている。 The communication passage 44b is a surface perpendicular to the direction of the gas action force F2, is below the gas action force surface S2 passing through the axis 9c2, and is opposite to the direction of the gas action force F2 (on the discharge port 49 side). Is provided.
　より詳細には、連絡通路４４ｂは、軸心９ｃ１を通り、反ガス作用力線Ｆ２’に対して下方に４５度の角度をなす第１傾斜線Ｌ６ａと、反ガス作用力線Ｆ２’に対して上方に４５度の角度をなす第２傾斜線Ｌ６ｂと、によって挟まれる範囲に設けられている。なおここで、軸心９ｃ１を通り、ガス作用力Ｆ２と軸心９ｃ１に対して反対の方向に延びる反ガス作用力線を反ガス作用力線Ｆ２’とする。 More specifically, the communication passage 44b passes through the shaft center 9c1 and is inclined with respect to the first inclined line L6a and the anti-gas action force line F2 ′ that form an angle of 45 degrees downward with respect to the anti-gas action force line F2 ′. And a second inclined line L6b that forms an angle of 45 degrees upward. Here, an anti-gas action force line F2 'passing through the axis 9c1 and extending in the opposite direction to the gas action force F2 and the axis 9c1 is referred to as an anti-gas action force line F2'.
　吐出側ロータ軸８ｃ、９ｃは、圧縮ガスから力を受けるようになっている。ここで、吐出側ロータ軸８ｃ、９ｃが上下方向に斜めに並んで配置されている場合でも、連絡通路４４ａ、４４ｂを、圧縮ガスから受けるガス作用力Ｆ１、Ｆ２の方向の反対側に設けることによって、ケーシング４による吐出側軸受部１６の支持力を低下させることなく、連絡通路４４ａ、４４ｂを設けることができる。 The discharge- side rotor shafts 8c and 9c are adapted to receive a force from the compressed gas. Here, even when the discharge- side rotor shafts 8c and 9c are arranged obliquely in the vertical direction, the communication passages 44a and 44b are provided on the side opposite to the direction of the gas acting forces F1 and F2 received from the compressed gas. Thus, the communication passages 44a and 44b can be provided without reducing the supporting force of the discharge-side bearing portion 16 by the casing 4.
　さらに、連絡通路４４ａ、４４ｂは、圧縮ガスから受けるガス作用力Ｆ１、Ｆ２の方向の反対側の所定の範囲、すなわち、軸心８ｃ１、９ｃ１を通り、反ガス作用力線Ｆ１’、Ｆ２’に対して下方に４５度の角度をなす第１傾斜線Ｌ５ａ、Ｌ６ａと、反ガス作用力線Ｆ１’、Ｆ２’に対して上方に４５度の角度をなす第２傾斜線Ｌ５ｂ、Ｌ６ｂと、によって挟まれる範囲に設けられている。連絡通路４４ａ、４４ｂをこの範囲に設けることによって、ケーシング４による吐出側軸受部１６の支持力を低下させることなく、連絡通路４４ａ、４４ｂを設けることができる。 Further, the communication passages 44a and 44b pass through a predetermined range opposite to the direction of the gas acting forces F1 and F2 received from the compressed gas, that is, through the shaft centers 8c1 and 9c1 and to the antigas acting force lines F1 ′ and F2 ′. With respect to the first inclined lines L5a and L6a that form an angle of 45 degrees downward with respect to the anti-gas action force lines F1 ′ and F2 ′, the second inclined lines L5b and L6b that form an angle of 45 degrees upward It is provided in the range to be sandwiched. By providing the communication passages 44a and 44b in this range, the communication passages 44a and 44b can be provided without reducing the supporting force of the discharge side bearing portion 16 by the casing 4.
（変形例）
　第１～第３実施形態では、吐出側ロータ軸８ｃ、９ｃの軸方向に垂直な断面において、連絡通路４４ａ、４４ｂは、円弧形状を有しているが、図７に示されるように、矩形を有していてもよい。また、連絡通路の大きさは特に限定されず、第１実施形態～第３実施形態に示される連絡通路より大きくても、小さくてもよい。また、図８に示されるように、複数の連絡通路４４ａが設けられてもよい。この場合、少なくとも１つの連絡通路４４ａの吐出側軸受部１６に接する部分の接触下端４４ａ１が、上下方向において、吐出側軸受部１６の内輪１８の内輪転送面の最下端１８ａと、吐出側軸受部１６の外輪２０の外輪転送面の最下端２０ａとの間に位置しているのが好ましい。また、より詳細には、少なくとも１つの連絡通路４４ａの接触下端４４ａ１が、吐出側軸受部１６の転動体２２の中心の軌道円２２ａの最下端２２ａ１と、吐出側軸受部１６の外輪転送面の最下端２０ａとの間に位置しているのがより好ましい。 (Modification)
In the first to third embodiments, in the cross section perpendicular to the axial direction of the discharge- side rotor shafts 8c and 9c, the communication passages 44a and 44b have an arc shape. However, as shown in FIG. You may have. Further, the size of the communication passage is not particularly limited, and may be larger or smaller than the communication passage shown in the first to third embodiments. Further, as shown in FIG. 8, a plurality of communication passages 44a may be provided. In this case, the contact lower end 44a1 of the portion in contact with the discharge side bearing portion 16 of the at least one communication passage 44a has the lowermost end 18a of the inner ring transfer surface of the inner ring 18 of the discharge side bearing portion 16 and the discharge side bearing portion in the vertical direction. It is preferable that the outer ring 20 is positioned between the lowermost ends 20a of the outer ring transfer surfaces of the sixteen outer rings 20. In more detail, the contact lower end 44a1 of the at least one communication passage 44a has the lowermost end 22a1 of the track circle 22a at the center of the rolling element 22 of the discharge side bearing portion 16 and the outer ring transfer surface of the discharge side bearing portion 16. More preferably, it is located between the lowermost end 20a.
　連絡通路の大きさを調整することによって、第１空間２４から第２空間２６への油の移動量を調整することができ、その結果、油面の位置を適切な位置に調整することができる。 By adjusting the size of the communication passage, the amount of movement of oil from the first space 24 to the second space 26 can be adjusted, and as a result, the position of the oil surface can be adjusted to an appropriate position. .
　また、複数の連絡通路を設けることによって、第１空間２４から第２空間２６への油の移動量が足りず油面が上昇した場合に、他の連絡通路からの油の移動量が増加することになり、その結果、油面の位置が大きく上昇することを防止できる。 Also, by providing a plurality of communication passages, when the amount of oil moving from the first space 24 to the second space 26 is insufficient and the oil level rises, the amount of oil movement from other communication passages increases. As a result, it is possible to prevent the oil level from rising greatly.
（別の実施形態）
　第１～第３実施形態では、吐出側について連絡通路４４ａ、４４ｂを設けることが示されているが、吸込側について、同様の連絡通路が設けられてもよい。図９は、吸込側に連絡通路が設けられる場合の油冷式スクリュ圧縮機２の平面部分断面図である。図１０は、図９のX-X線に沿った部分断面図である。別の実施形態は、吸込側に連絡通路が設けられる点で第１～第３実施形態と異なっており、その他の構成は第１～第３実施形態と同じである。このため、この変形例の説明においては、上記実施形態と同じ部分には同じ符号を付し、それらの内容については詳しい説明を省略する。 (Another embodiment)
In the first to third embodiments, it is shown that the communication passages 44a and 44b are provided on the discharge side, but a similar communication passage may be provided on the suction side. FIG. 9 is a plan partial sectional view of the oil-cooled screw compressor 2 when a communication passage is provided on the suction side. 10 is a partial cross-sectional view taken along line XX of FIG. Another embodiment is different from the first to third embodiments in that a communication passage is provided on the suction side, and the other configurations are the same as those of the first to third embodiments. For this reason, in the description of this modification, the same reference numerals are given to the same portions as those in the above-described embodiment, and detailed descriptions thereof are omitted.
　図９及び図１０に示されるように、ケーシング４内には、圧縮室６、軸受室１０と共に、吸込側軸受室１１が形成されている。吸込側ロータ軸８ｂ、９ｂとケーシング４との間には、吸込側軸封部３９が配設されており、圧縮室６と吸込側軸受室１１との間を隔離している。吸込側軸受室１１には、吸込側ロータ軸８ｂ、９ｂを回転自在に支持する吸込側軸受部３５が収容されている。吸込側軸受部３５は、吐出側軸受部１６と同様、リング状の内輪と、リング状の外輪と、それらの間に配置された球状または円柱状の転動体とを備える。そして、吸込側軸受部３５によって吸込側軸受室１１内が、吸込側軸受部３５の軸方向端部とケーシング４との間に設けられる第３空間３８と、吸込側軸封部３９とに仕切られている。 9 and 10, a suction side bearing chamber 11 is formed in the casing 4 together with the compression chamber 6 and the bearing chamber 10. A suction side shaft sealing portion 39 is disposed between the suction side rotor shafts 8 b and 9 b and the casing 4, and isolates the compression chamber 6 from the suction side bearing chamber 11. The suction side bearing chamber 11 accommodates a suction side bearing portion 35 that rotatably supports the suction side rotor shafts 8b and 9b. Similarly to the discharge-side bearing portion 16, the suction-side bearing portion 35 includes a ring-shaped inner ring, a ring-shaped outer ring, and a spherical or cylindrical rolling element disposed therebetween. Then, the suction side bearing portion 35 divides the inside of the suction side bearing chamber 11 into a third space 38 provided between the axial end portion of the suction side bearing portion 35 and the casing 4 and a suction side shaft sealing portion 39. It has been.
　スクリュ圧縮機２は、雄ロータ８の吸込側ロータ軸８ｂがケーシング４の外側に延伸し、不図示のモータ等に接続されている。一方、雌ロータ９の吸込側ロータ軸９ｂの端部は、ケーシング４内に収容されている。吸込側ロータ軸９ｂの端部には、スラスト荷重を受け止めるための軸受内輪抑え４１が設けられている。軸受内輪抑え４１は、吸込側軸受部３５の内輪と当接し、内輪の軸方向の移動を制限している。 In the screw compressor 2, the suction-side rotor shaft 8b of the male rotor 8 extends to the outside of the casing 4, and is connected to a motor or the like (not shown). On the other hand, the end of the suction side rotor shaft 9 b of the female rotor 9 is accommodated in the casing 4. A bearing inner ring restrainer 41 for receiving a thrust load is provided at the end of the suction side rotor shaft 9b. The bearing inner ring restraint 41 is in contact with the inner ring of the suction side bearing portion 35 and restricts the movement of the inner ring in the axial direction.
　また、ケーシング４には、給油口４０が設けられている。給油口４０は、軸封給油口３４と同様にケーシング４を貫通して設けられている。給油口４０は、吸込側軸受部３５に油を供給するため、第３空間３８と連通している。 Further, the casing 4 is provided with a fuel filler port 40. Similar to the shaft-sealed oil supply port 34, the oil supply port 40 is provided so as to penetrate the casing 4. The oil supply port 40 communicates with the third space 38 in order to supply oil to the suction side bearing portion 35.
　スクリュ圧縮機２は、第３空間３８に溜まった油を排油するため、第３空間３８と、吸込空間４８とを連通する第２連絡通路４４ｃ、４４ｄを備えている。第２連絡通路４４ｃ、４４ｄは、ケーシング４に切欠きを設けることによって形成されており、それぞれ、直線状に延びており、吸込側ロータ軸８ｂ、９ｂと平行である長手方向軸を有している。吸込側ロータ軸８ｂ、９ｂの軸方向に垂直な断面において、第２連絡通路４４ｃ、４４ｄは円弧形状を有している。 The screw compressor 2 includes second communication passages 44 c and 44 d that connect the third space 38 and the suction space 48 in order to drain the oil accumulated in the third space 38. The second communication passages 44c and 44d are formed by providing a cutout in the casing 4, each extending linearly and having a longitudinal axis parallel to the suction- side rotor shafts 8b and 9b. Yes. In the cross section perpendicular to the axial direction of the suction- side rotor shafts 8b and 9b, the second communication passages 44c and 44d have an arc shape.
　そして、図４～図８で述べられた連絡通路４４ａ、４４ｂの配置については、吸込側に設けられた第２連絡通路４４ｃ、４４ｄにも同様に適用できる。すなわち、図４～図８において示された吐出側ロータ軸８ｃ、９ｃを吸込側ロータ軸８ｂ、９ｂに置き換えることで、吸込側の第２連絡通路４４ｃ、４４ｄについて、同様に説明できる。 The arrangement of the communication passages 44a and 44b described in FIGS. 4 to 8 can be similarly applied to the second communication passages 44c and 44d provided on the suction side. That is, by replacing the discharge side rotor shafts 8c and 9c shown in FIGS. 4 to 8 with the suction side rotor shafts 8b and 9b, the suction side second communication passages 44c and 44d can be similarly explained.
　図４に示されるように、吸込側ロータ軸８ｂ、９ｂが水平方向に並んで配置されるスクリュ圧縮機２によれば、次のような効果を発揮できる。 As shown in FIG. 4, according to the screw compressor 2 in which the suction side rotor shafts 8b and 9b are arranged in the horizontal direction, the following effects can be exhibited.
（１）第３空間３８と吸込空間４８とを連通する第２連絡通路４４ｃ、４４ｄを備えているので、第３空間３８である吸込側軸受部３５上流側の余分な油が吸込空間４８に移動することにより、吸込側軸受部３５上流側における油の撹拌ロスを低減できる。 (1) Since the second communication passages 44 c and 44 d communicating the third space 38 and the suction space 48 are provided, excess oil on the upstream side of the suction side bearing portion 35, which is the third space 38, enters the suction space 48. By moving, oil agitation loss on the upstream side of the suction side bearing portion 35 can be reduced.
（２）第２連絡通路４４ｃ、４４ｄの吸込側軸受部３５に接する部分の接触下端４４ａ１、４４ｂ１を吸込側軸受部３５の内輪転送面の最下端１８ａと外輪転送面の最下端２０ａとの間に配置することによって、第３空間３８の油面位置を転動体２２が油浴する高さに保持することができ、必要な油量を吸込側軸受部３５に供給しながら、第２連絡通路４４ｃ、４４ｄによって余分な油を吸込空間４８に移動させることができる。 (2) The contact lower ends 44a1 and 44b1 of the portions of the second communication passages 44c and 44d that are in contact with the suction side bearing portion 35 are located between the lowermost end 18a of the inner ring transfer surface of the suction side bearing portion 35 and the lowermost end 20a of the outer ring transfer surface. The oil level position of the third space 38 can be maintained at a height at which the rolling elements 22 bathe, and the second communication passage is supplied to the suction-side bearing portion 35 while supplying the required amount of oil. Excess oil can be moved to the suction space 48 by 44c and 44d.
（３）第２連絡通路４４ｃ、４４ｄの接触下端４４ａ１、４４ｂ１を吸込側軸受部３５の転動体２２の中心の軌道円の最下端２２ａ１と外輪転送面の最下端２０ａとの間に配置することによって、第３空間３８の油面位置を転動体２２の中心位置から外輪転送面までの間に保持することができ、必要かつより少量の油量を吸込側軸受部３５に供給しながら、第２連絡通路４４ｃ、４４ｄによって余分な油を吸込空間４８に移動させることができる。 (3) The contact lower ends 44a1 and 44b1 of the second communication passages 44c and 44d are disposed between the lowermost end 22a1 of the orbital circle at the center of the rolling element 22 of the suction side bearing portion 35 and the lowermost end 20a of the outer ring transfer surface. Thus, the oil level position of the third space 38 can be held between the center position of the rolling elements 22 and the outer ring transfer surface, and the necessary and smaller amount of oil is supplied to the suction side bearing portion 35 while The excess oil can be moved to the suction space 48 by the two communication passages 44c and 44d.
（４）吸込側ロータ軸８ｂ、９ｂは、圧縮ガスから力を受けるようになっている。ここで、第２連絡通路４４ｃ、４４ｄを、ガス作用力面Ｓ１、Ｓ２の下方、すなわち、圧縮ガスから受けるガス作用力Ｆ１、Ｆ２の方向の反対側（吐出ポート４９側）に設けることによって、ケーシング４による吸込側軸受部３５の支持力を低下させることなく、第２連絡通路４４ｃ、４４ｄを設けることができる。 (4) The suction side rotor shafts 8b and 9b are adapted to receive force from the compressed gas. Here, by providing the second communication passages 44c and 44d below the gas acting force surfaces S1 and S2, that is, on the opposite side of the direction of the gas acting forces F1 and F2 received from the compressed gas (on the discharge port 49 side), The second communication passages 44c and 44d can be provided without reducing the supporting force of the suction side bearing portion 35 by the casing 4.
（５）第２連絡通路４４ｃ、４４ｄは、圧縮ガスから受けるガス作用力Ｆ１、Ｆ２の方向の反対側の所定の範囲、すなわち、軸心８ｃ１、９ｃ１を通り、反ガス作用力線Ｆ１’、Ｆ２’に対して下方に４５度の角度をなす第１傾斜線Ｆ１’ａ、Ｆ２’ａと、反ガス作用力線Ｆ１’、Ｆ２’に対して上方に４５度の角度をなす第２傾斜線Ｆ１’ｂ、Ｆ２’ｂと、によって挟まれる範囲に設けられている。第２連絡通路４４ｃ、４４ｄをこの範囲に設けることによって、ケーシング４による吸込側軸受部３５の支持力を低下させることなく、第２連絡通路４４ｃ、４４ｄを設けることができる。 (5) The second communication passages 44c and 44d pass through a predetermined range on the opposite side to the direction of the gas acting forces F1 and F2 received from the compressed gas, that is, through the shaft centers 8c1 and 9c1, and the antigas acting force lines F1 ′, First inclination lines F1′a and F2′a that form an angle of 45 degrees downward with respect to F2 ′, and a second inclination that forms an angle of 45 degrees with respect to the anti-gas action force lines F1 ′ and F2 ′. It is provided in a range sandwiched between the lines F1′b and F2′b. By providing the second communication passages 44c and 44d in this range, the second communication passages 44c and 44d can be provided without reducing the support force of the suction side bearing portion 35 by the casing 4.
（６）第２連絡通路４４ｃ、４４ｄは、直線状に延びており、吸込側ロータ軸８ｂ、９ｂと平行である長手方向軸を有している。第２連絡通路４４ｃ、４４ｄを機械加工で製作する場合、ケーシング４の外部方向から１度の機械加工で製作することができるので、第２連絡通路４４ｃ、４４ｄの製作性及び製造コストを有利とすることができる。また、第２連絡通路４４ｃ、４４ｄを鋳物で製作する場合であっても、簡単な構造であるため、鋳型の抜き方向を考慮することなく、軸受保持穴の型の一部を改造するだけで製作が可能であり、第２連絡通路４４ｃ、４４ｄの製作性及び製造コストを有利とすることができる。 (6) The second communication passages 44c and 44d extend linearly and have a longitudinal axis parallel to the suction side rotor shafts 8b and 9b. When the second connecting passages 44c and 44d are manufactured by machining, the second connecting passages 44c and 44d can be manufactured by one machining from the outside of the casing 4, so that the manufacturability and manufacturing cost of the second connecting passages 44c and 44d are advantageous. can do. Even when the second communication passages 44c and 44d are made of cast metal, since the structure is simple, it is only necessary to modify a part of the bearing holding hole mold without considering the mold drawing direction. Manufacture is possible, and the manufacturability and manufacturing cost of the second communication passages 44c and 44d can be advantageous.
　図５に示されるように、吸込側ロータ軸８ｂ、９ｂが上下方向に並んで配置されるスクリュ圧縮機２によれば、次のような効果を発揮できる。 As shown in FIG. 5, according to the screw compressor 2 in which the suction side rotor shafts 8b and 9b are arranged in the vertical direction, the following effects can be exhibited.
　吸込側ロータ軸８ｂ、９ｂは、圧縮ガスから力を受けるようになっている。ここで、吸込側ロータ軸８ｂ、９ｂが上下方向に並んで配置されている場合でも、第２連絡通路４４ｃ、４４ｄを、圧縮ガスから受けるガス作用力Ｆ１、Ｆ２の方向の反対側に設けることによって、ケーシング４による吸込側軸受部３５の支持力を低下させることなく、第２連絡通路４４ｃ、４４ｄを設けることができる。 The suction- side rotor shafts 8b and 9b are adapted to receive a force from the compressed gas. Here, even when the suction- side rotor shafts 8b and 9b are arranged side by side in the vertical direction, the second communication passages 44c and 44d are provided on the side opposite to the direction of the gas acting forces F1 and F2 received from the compressed gas. Thus, the second communication passages 44c and 44d can be provided without reducing the supporting force of the suction side bearing portion 35 by the casing 4.
　図６に示されるように、吸込側ロータ軸８ｂ、９ｂが上下方向に斜めに並んで配置されるスクリュ圧縮機２によれば、次のような効果を発揮できる。 As shown in FIG. 6, according to the screw compressor 2 in which the suction side rotor shafts 8b and 9b are arranged obliquely in the vertical direction, the following effects can be exhibited.
　吸込側ロータ軸８ｂ、９ｂは、圧縮ガスから力を受けるようになっている。ここで、吸込側ロータ軸８ｂ、９ｂが上下方向に斜めに並んで配置されている場合でも、第２連絡通路４４ｃ、４４ｄを、圧縮ガスから受けるガス作用力Ｆ１、Ｆ２の方向の反対側に設けることによって、ケーシング４による吸込側軸受部３５の支持力を低下させることなく、第２連絡通路４４ｃ、４４ｄを設けることができる。 The suction- side rotor shafts 8b and 9b are adapted to receive a force from the compressed gas. Here, even when the suction- side rotor shafts 8b and 9b are arranged obliquely in the vertical direction, the second communication passages 44c and 44d are disposed on the opposite side of the direction of the gas acting forces F1 and F2 received from the compressed gas. By providing, the second communication passages 44c and 44d can be provided without reducing the supporting force of the suction side bearing portion 35 by the casing 4.
　さらに、第２連絡通路４４ｃ、４４ｄは、圧縮ガスから受けるガス作用力Ｆ１、Ｆ２の方向の反対側の所定の範囲、すなわち、軸心８ｃ１、９ｃ１を通り、反ガス作用力線Ｆ１’、Ｆ２’に対して下方に４５度の角度をなす第１傾斜線Ｌ５ａ、Ｌ６ａと、反ガス作用力線Ｆ１’、Ｆ２’に対して上方に４５度の角度をなす第２傾斜線Ｌ５ｂ、Ｌ６ｂと、によって挟まれる範囲に設けられている。第２連絡通路４４ｃ、４４ｄをこの範囲に設けることによって、ケーシング４による吸込側軸受部３５の支持力を低下させることなく、第２連絡通路４４ｃ、４４ｄを設けることができる。 Further, the second communication passages 44c and 44d pass through a predetermined range opposite to the direction of the gas acting forces F1 and F2 received from the compressed gas, that is, pass through the shaft centers 8c1 and 9c1, and antigas acting force lines F1 ′ and F2 First inclined lines L5a and L6a which form an angle of 45 degrees downward with respect to ', and second inclined lines L5b and L6b which form an angle of 45 degrees upward with respect to the anti-gas action force lines F1' and F2 '; , Are provided in a range between. By providing the second communication passages 44c and 44d in this range, the second communication passages 44c and 44d can be provided without reducing the support force of the suction side bearing portion 35 by the casing 4.
　第１～第３実施形態では、吐出側について連絡通路４４ａ、４４ｂを設けることが示されているが、別の実施形態では、吸込側について第２連絡通路４４ｃ、４４ｄを設けることが示されている。本発明では、吐出側のみ連絡通路４４ａ、４４ｂを設けてもよく、吸込側のみ第２連絡通路４４ｃ、４４ｄを設けてもよく、また、吐出側及び吸込側の両方に連絡通路を設けてもよい。そして、吐出側及び吸込側の両方に連絡通路を設ける場合には、連絡通路４４ａ、４４ｂと第２連絡通路４４ｃ、４４ｄとは、スクリュロータ８、９の軸方向から見て重なる位置に設けられていることが好ましい。本構成によれば、ケーシング４による吐出側軸受部１６及び吸込側軸受部３５の支持力を両方共低下させることなく、連絡通路４４ａ、４４ｂ及び第２連絡通路４４ｃ、４４ｄを設けることができる。なお、連絡通路４４ａ、４４ｂと第２連絡通路４４ｃ、４４ｄとが、スクリュロータ８、９の軸方向から見て重なる位置に設けられているとは、連絡通路４４ａ、４４ｂと第２連絡通路４４ｃ、４４ｄとが、スクリュロータ８、９の軸方向から見て一部が重なっていればよい。 In the first to third embodiments, it is shown that the communication passages 44a and 44b are provided on the discharge side. However, in another embodiment, the second communication passages 44c and 44d are shown on the suction side. Yes. In the present invention, the communication passages 44a and 44b may be provided only on the discharge side, the second communication passages 44c and 44d may be provided only on the suction side, or the communication passages may be provided on both the discharge side and the suction side. Good. When the communication passages are provided on both the discharge side and the suction side, the communication passages 44a and 44b and the second communication passages 44c and 44d are provided at positions overlapping each other when viewed from the axial direction of the screw rotors 8 and 9. It is preferable. According to this configuration, the communication passages 44 a and 44 b and the second communication passages 44 c and 44 d can be provided without reducing both the supporting forces of the discharge side bearing portion 16 and the suction side bearing portion 35 by the casing 4. Note that the communication passages 44a and 44b and the second communication passages 44c and 44d are provided at positions overlapping each other when viewed from the axial direction of the screw rotors 8 and 9. , 44d need only partially overlap each other when viewed from the axial direction of the screw rotors 8,9.
（別の実施形態の変形例）
　別の実施形態では、吸込側ロータ軸８ｂ、９ｂの軸方向に垂直な断面において、第２連絡通路４４ｃ、４４ｄは、円弧形状を有しているが、図７に示されるように、矩形を有していてもよい。また、第２連絡通路の大きさは特に限定されず、別の実施形態に示される第２連絡通路より大きくても、小さくてもよい。また、図８に示されるように、複数の第２連絡通路４４ｃが設けられてもよい。この場合、少なくとも１つの第２連絡通路４４ｃの吸込側軸受部３５に接する部分の接触下端４４ａ１が、上下方向において、吸込側軸受部３５の内輪１８の内輪転送面の最下端１８ａと、吸込側軸受部３５の外輪２０の外輪転送面の最下端２０ａとの間に位置しているのが好ましい。また、より詳細には、少なくとも１つの第２連絡通路４４ｃの接触下端４４ａ１が、吸込側軸受部３５の転動体２２の中心の軌道円２２ａの最下端２２ａ１と、吸込側軸受部３５の外輪転送面の最下端２０ａとの間に位置しているのがより好ましい。 (Modification of another embodiment)
In another embodiment, in the cross section perpendicular to the axial direction of the suction side rotor shafts 8b and 9b, the second communication passages 44c and 44d have an arc shape, but as shown in FIG. You may have. In addition, the size of the second communication passage is not particularly limited, and may be larger or smaller than the second communication passage shown in another embodiment. Moreover, as shown in FIG. 8, a plurality of second communication passages 44c may be provided. In this case, the contact lower end 44a1 of the portion in contact with the suction side bearing portion 35 of at least one second communication passage 44c is in the vertical direction with the lowest end 18a of the inner ring transfer surface of the inner ring 18 of the suction side bearing portion 35 and the suction side. It is preferable that the bearing portion 35 is located between the outermost ring transfer surface of the outer ring 20 and the lowermost end 20a. More specifically, the contact lower end 44a1 of at least one second communication passage 44c is connected to the lowermost end 22a1 of the track circle 22a at the center of the rolling element 22 of the suction side bearing portion 35 and the outer ring transfer of the suction side bearing portion 35. More preferably, it is located between the lowermost end 20a of the surface.
　第２連絡通路の大きさを調整することによって、第３空間３８から吸込空間４８への油の移動量を調整することができ、その結果、油面の位置を適切な位置に調整することができる。 By adjusting the size of the second communication passage, the amount of movement of oil from the third space 38 to the suction space 48 can be adjusted, and as a result, the position of the oil surface can be adjusted to an appropriate position. it can.
　また、複数の第２連絡通路を設けることによって、第３空間３８から吸込空間４８への油の移動量が足りず油面が上昇した場合に、他の第２連絡通路からの油の移動量が増加することになり、その結果、油面の位置が大きく上昇することを防止できる。 Also, by providing a plurality of second communication passages, the amount of oil movement from the other second communication passages when the amount of oil movement from the third space 38 to the suction space 48 is insufficient and the oil level rises. As a result, it is possible to prevent the oil level from greatly rising.
　本発明は、上記実施形態で説明した構成には限定されず、特許請求の範囲に記載した内容を逸脱することなく、当業者が考え得る各種変形例を含むことができる。 The present invention is not limited to the configuration described in the above embodiment, and can include various modifications that can be considered by those skilled in the art without departing from the content described in the claims.
　　２　油冷式スクリュ圧縮機　
　　４　ケーシング　
　　６　圧縮室　
　　８　雄ロータ（スクリュロータ）　
　　８ａ　雄ロータ本体　
　　８ｂ　吸込側ロータ軸　
　　８ｃ　吐出側ロータ軸　
　　８ｄ　吐出端面　
　　８ｅ　歯溝部　
　　８ｆ　吸込端面　
　　９　雌ロータ（スクリュロータ）　
　　９ａ　雌ロータ本体　
　　９ｂ　吸込側ロータ軸　
　　９ｃ　吐出側ロータ軸　
　　９ｄ　吐出端面　
　　９ｆ　吸込端面　
　　１０　軸受室　
　　１１　吸込側軸受室　
　　１４　軸封部　
　　１６　吐出側軸受部　
　　１８　内輪　
　　１８ａ　内輪転送面の最下端　
　　２０　外輪　
　　２０ａ　外輪転送面の最下端　
　　２２　転動体　
　　２２ａ　軌道円　
　　２２ａ１　最下端　
　　２４　軸受上流空間（第１空間）　
　　２６　軸受下流空間（第２空間）　
　　２８　軸受内輪抑え　
　　３０　軸受外輪抑え　
　　３２　ロータ給油口　
　　３４　軸封給油口　
　　３５　吸込側軸受部　
　　３８　第３空間　
　　３９　吸込側軸封部　
　　４０　給油口　
　　４１　軸受内輪抑え　
　　４４ａ　連絡通路　
　　４４ｂ　連絡通路　
　　４４ｃ　第２連絡通路　
　　４４ｄ　第２連絡通路　
　　４６　排油通路　
　　４８　吸込空間　
　　４９　吐出ポート　
　　５０　吐出口　 2 Oil-cooled screw compressor
4 Casing
6 Compression chamber
8 Male rotor (screw rotor)
8a Male rotor body
8b Suction side rotor shaft
8c Discharge-side rotor shaft
8d Discharge end face
8e tooth gap
8f Suction end face
9 Female rotor (screw rotor)
9a Female rotor body
9b Suction side rotor shaft
9c Discharge-side rotor shaft
9d Discharge end face
9f Suction end face
10 Bearing room
11 Suction side bearing chamber
14 Shaft seal
16 Discharge side bearing
18 Inner ring
18a Bottom end of inner ring transfer surface
20 Outer ring
20a Bottom end of outer ring transfer surface
22 Rolling elements
22a orbit circle
22a1 bottom end
24 Bearing upstream space (first space)
26 Bearing downstream space (second space)
28 Bearing inner ring restraint
30 Bearing outer ring restraint
32 Rotor filler
34 Shaft seal filler
35 Suction side bearing
38 3rd space
39 Suction side shaft seal
40 Refueling port
41 Bearing inner ring restraint
44a Connecting passage
44b Connecting passage
44c Second communication passage
44d Second communication passage
46 Oil drainage passage
48 Suction space
49 Discharge port
50 Discharge port

Claims (15)

  1. 　噛み合い状態で回転してガスを圧縮する一対のスクリュロータと、
    　前記一対のスクリュロータを収容するケーシングと、
    　前記スクリュロータの吐出側ロータ軸を支持する吐出側軸受部と、
    　前記吐出側ロータ軸を軸封する軸封部と、
    　前記軸封部と前記吐出側軸受部との間に設けられる第１空間と、
    　前記吐出側軸受部の軸方向端部と前記ケーシングとの間に設けられる第２空間と、
    　前記ケーシングに形成され、前記第１空間と前記第２空間とを連通する連絡通路と、を備えていることを特徴とする、油冷式スクリュ圧縮機。     A pair of screw rotors that rotate in mesh and compress gas;
    A casing for accommodating the pair of screw rotors;
    A discharge-side bearing portion that supports a discharge-side rotor shaft of the screw rotor;
    A shaft seal portion for sealing the discharge-side rotor shaft;
    A first space provided between the shaft sealing portion and the discharge-side bearing portion;
    A second space provided between an axial end of the discharge side bearing portion and the casing;
    An oil-cooled screw compressor, comprising: a communication passage formed in the casing and communicating with the first space and the second space.
  2. 　前記連絡通路の前記吐出側軸受部に接する部分の接触下端は、前記吐出側軸受部の内輪転送面の最下端と、前記吐出側軸受部の外輪転送面の最下端との間に位置している、請求項１記載の油冷式スクリュ圧縮機。 The lower contact portion of the communication passage in contact with the discharge side bearing portion is located between the lowermost end of the inner ring transfer surface of the discharge side bearing portion and the lowermost end of the outer ring transfer surface of the discharge side bearing portion. The oil-cooled screw compressor according to claim 1.
  3. 　前記接触下端は、前記吐出側軸受部の転動体の中心の軌道円の最下端と、前記吐出側軸受部の外輪転送面の最下端との間に位置している、請求項２記載の油冷式スクリュ圧縮機。 3. The oil according to claim 2, wherein the contact lower end is located between a lowermost end of a raceway circle at a center of a rolling element of the discharge side bearing portion and a lowermost end of an outer ring transfer surface of the discharge side bearing portion. Cold screw compressor.
  4. 　前記吐出側ロータ軸の軸方向に垂直な断面において、
    　前記一対のスクリュロータにより圧縮された圧縮ガスを排出する吐出ポートは、前記吐出側ロータ軸の軸心を結ぶ直線に対して下方又は側方に配置され、
    　前記連絡通路は、圧縮ガスによって前記吐出側ロータ軸に作用するガス作用力の方向に垂直な面であって、前記吐出側ロータ軸の軸心を通る、ガス作用力面に対して前記吐出ポート側に設けられている、請求項１記載の油冷式スクリュ圧縮機。     In a cross section perpendicular to the axial direction of the discharge-side rotor shaft,
    The discharge port for discharging the compressed gas compressed by the pair of screw rotors is disposed below or laterally with respect to a straight line connecting the axis of the discharge side rotor shaft,
    The communication passage is a surface perpendicular to the direction of the gas acting force acting on the discharge side rotor shaft by the compressed gas, and passes through the axis of the discharge side rotor shaft, and the discharge port with respect to the gas acting force surface The oil-cooled screw compressor according to claim 1, which is provided on a side.
  5. 　前記吐出側ロータ軸の軸方向に垂直な断面において、
    　前記吐出側ロータ軸の軸心を結ぶ直線と水平線とのなす角度は、０度以上４５度以下であり、
    　前記連絡通路は、前記軸心を通り、前記軸心に対して前記ガス作用力と反対の方向に延びる反ガス作用力線に対して下方に４５度の角度をなす第１傾斜線と、前記反ガス作用力線に対して上方に４５度の角度をなす第２傾斜線と、によって挟まれる範囲に設けられている、請求項４記載の油冷式スクリュ圧縮機。     In a cross section perpendicular to the axial direction of the discharge-side rotor shaft,
    An angle formed by a straight line connecting the axis of the discharge-side rotor shaft and a horizontal line is 0 degree or more and 45 degrees or less,
    The communication passage passes through the axis and has a first inclined line that forms an angle of 45 degrees downward with respect to an anti-gas action force line extending in a direction opposite to the gas action force with respect to the axis; The oil-cooled screw compressor according to claim 4, wherein the oil-cooled screw compressor is provided in a range sandwiched by a second inclined line that forms an angle of 45 degrees upward with respect to the anti-gas acting force line.
  6. 　前記連絡通路は、直線状に延びており、前記吐出側ロータ軸と平行である長手方向軸を有している、請求項１～５のいずれか１つに記載の油冷式スクリュ圧縮機。 The oil-cooled screw compressor according to any one of claims 1 to 5, wherein the communication passage extends in a straight line and has a longitudinal axis parallel to the discharge-side rotor shaft.
  7. 　前記連絡通路を複数備えている、請求項１～３のいずれか１つに記載の油冷式スクリュ圧縮機。 The oil-cooled screw compressor according to any one of claims 1 to 3, comprising a plurality of the communication passages.
  8. 　噛み合い状態で回転してガスを圧縮する一対のスクリュロータと、
    　前記一対のスクリュロータを収容するケーシングと、
    　前記スクリュロータの吸込側ロータ軸を支持する吸込側軸受部と、
    　前記吸込側軸受部の軸方向端部と前記ケーシングとの間に設けられる第３空間と、
    　前記スクリュロータがガスを吸い込む吸込空間と、
    　前記ケーシングに形成され、前記第３空間と前記吸込空間とを連通する第２連絡通路と、を備えていることを特徴とする、油冷式スクリュ圧縮機。     A pair of screw rotors that rotate in mesh and compress gas;
    A casing for accommodating the pair of screw rotors;
    A suction side bearing portion that supports a suction side rotor shaft of the screw rotor;
    A third space provided between the axial end of the suction side bearing portion and the casing;
    A suction space into which the screw rotor sucks gas;
    An oil-cooled screw compressor, comprising: a second communication passage formed in the casing and communicating with the third space and the suction space.
  9. 　前記第２連絡通路の前記吸込側軸受部に接する部分の接触下端は、前記吸込側軸受部の内輪転送面の最下端と、前記吸込側軸受部の外輪転送面の最下端との間に位置している、請求項８記載の油冷式スクリュ圧縮機。 The contact lower end of the portion of the second communication passage that is in contact with the suction side bearing portion is located between the lowermost end of the inner ring transfer surface of the suction side bearing portion and the lowermost end of the outer ring transfer surface of the suction side bearing portion. The oil-cooled screw compressor according to claim 8.
  10. 　前記接触下端は、前記吸込側軸受部の転動体の中心の軌道円の最下端と、前記吸込側軸受部の外輪転送面の最下端との間に位置している、請求項９記載の油冷式スクリュ圧縮機。 The oil according to claim 9, wherein the lower end of the contact is located between a lowermost end of a track circle at a center of a rolling element of the suction side bearing portion and a lowermost end of an outer ring transfer surface of the suction side bearing portion. Cold screw compressor.
  11. 　前記吸込側ロータ軸の軸方向に垂直な断面において、
    　前記一対のスクリュロータにより圧縮された圧縮ガスを排出する吐出ポートは、前記吸込側ロータ軸の軸心を結ぶ直線に対して下方又は側方に配置され、
    　前記第２連絡通路は、圧縮ガスによって前記吸込側ロータ軸に作用するガス作用力の方向に垂直な面であって、前記吸込側ロータ軸の軸心を通る、ガス作用力面に対して前記吐出ポート側に設けられている、請求項８記載の油冷式スクリュ圧縮機。     In a cross section perpendicular to the axial direction of the suction side rotor shaft,
    The discharge port for discharging the compressed gas compressed by the pair of screw rotors is disposed below or laterally with respect to a straight line connecting the axis of the suction side rotor shaft,
    The second communication passage is a surface perpendicular to the direction of the gas acting force acting on the suction side rotor shaft by the compressed gas, and passes through the axial center of the suction side rotor shaft and the gas acting force surface. The oil-cooled screw compressor according to claim 8, which is provided on the discharge port side.
  12. 　前記吸込側ロータ軸の軸方向に垂直な断面において、
    　前記吸込側ロータ軸の軸心を結ぶ直線と水平線とのなす角度は、０度以上４５度以下であり、
    　前記第２連絡通路は、前記軸心を通り、前記軸心に対して前記ガス作用力と反対の方向に延びる反ガス作用力線に対して下方に４５度の角度をなす第１傾斜線と、前記反ガス作用力線に対して上方に４５度の角度をなす第２傾斜線と、によって挟まれる範囲に設けられている、請求項１１記載の油冷式スクリュ圧縮機。     In a cross section perpendicular to the axial direction of the suction side rotor shaft,
    An angle formed by a straight line connecting the axis of the suction side rotor shaft and a horizontal line is 0 degree or more and 45 degrees or less,
    The second communication passage includes a first inclined line that passes through the axis and forms an angle of 45 degrees downward with respect to an anti-gas action force line extending in a direction opposite to the gas action force with respect to the axis. The oil-cooled screw compressor according to claim 11, wherein the oil-cooled screw compressor is provided in a range sandwiched between a second inclined line that forms an angle of 45 degrees upward with respect to the anti-gas acting force line.
  13. 　前記第２連絡通路は、直線状に延びており、前記吸込側ロータ軸と平行である長手方向軸を有している、請求項８～１２のいずれか１つに記載の油冷式スクリュ圧縮機。 The oil-cooled screw compression according to any one of claims 8 to 12, wherein the second communication passage extends linearly and has a longitudinal axis parallel to the suction-side rotor shaft. Machine.
  14. 　前記第２連絡通路を複数備えている、請求項８～１０のいずれか１つに記載の油冷式スクリュ圧縮機。 The oil-cooled screw compressor according to any one of claims 8 to 10, comprising a plurality of the second communication passages.
  15. 　噛み合い状態で回転してガスを圧縮する一対のスクリュロータと、
    　前記一対のスクリュロータを収容するケーシングと、
    　前記スクリュロータの吐出側ロータ軸を支持する吐出側軸受部と、
    　前記吐出側ロータ軸を軸封する軸封部と、
    　前記軸封部と前記吐出側軸受部との間に設けられる第１空間と、
    　前記吐出側軸受部の軸方向端部と前記ケーシングとの間に設けられる第２空間と、
    　前記ケーシングに形成され、前記第１空間と前記第２空間とを連通する連絡通路と、
    　前記スクリュロータの吸込側ロータ軸を支持する吸込側軸受部と、
    　前記吸込側軸受部の軸方向端部と前記ケーシングとの間に設けられる第３空間と、
    　前記スクリュロータがガスを吸い込む吸込空間と、
    　前記ケーシングに形成され、前記第３空間と前記吸込空間とを連通する第２連絡通路と、を備え、
    　前記連絡通路と前記第２連絡通路とは、前記スクリュロータの軸方向から見て重なる位置に設けられていることを特徴とする、油冷式スクリュ圧縮機。     A pair of screw rotors that rotate in mesh and compress gas;
    A casing for accommodating the pair of screw rotors;
    A discharge-side bearing portion that supports a discharge-side rotor shaft of the screw rotor;
    A shaft seal portion for sealing the discharge-side rotor shaft;
    A first space provided between the shaft sealing portion and the discharge-side bearing portion;
    A second space provided between an axial end of the discharge side bearing portion and the casing;
    A communication passage formed in the casing and communicating between the first space and the second space;
    A suction side bearing portion that supports a suction side rotor shaft of the screw rotor;
    A third space provided between the axial end of the suction side bearing portion and the casing;
    A suction space into which the screw rotor sucks gas;
    A second communication passage formed in the casing and communicating with the third space and the suction space;
    The oil-cooled screw compressor, wherein the communication passage and the second communication passage are provided at positions overlapping each other when viewed from the axial direction of the screw rotor.
PCT/JP2018/000855 2017-01-17 2018-01-15 Oil-cooled screw compressor WO2018135444A1 (en)

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Citations (3)

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JP4546136B2 (en) 2004-04-22 2010-09-15 株式会社神戸製鋼所 Screw refrigeration equipment
CN102356240B (en) * 2009-03-16 2015-03-11 大金工业株式会社 Screw compressor
JP5844980B2 (en) * 2011-02-15 2016-01-20 株式会社神戸製鋼所 Two-stage screw compression refrigeration system
JP5950870B2 (en) * 2013-06-20 2016-07-13 株式会社神戸製鋼所 Oil-cooled screw compressor

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JP2006144781A (en) * 2004-10-21 2006-06-08 Hitachi Industrial Equipment Systems Co Ltd Air compressor lubricating device, and air compressor with the same
JP2007126993A (en) * 2005-11-01 2007-05-24 Toyota Industries Corp Vacuum pump
JP2011001937A (en) * 2009-06-22 2011-01-06 Kobe Steel Ltd Screw compressor

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