WO2020240678A1 - Compresseur à vis - Google Patents

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Publication number
WO2020240678A1
WO2020240678A1 PCT/JP2019/020999 JP2019020999W WO2020240678A1 WO 2020240678 A1 WO2020240678 A1 WO 2020240678A1 JP 2019020999 W JP2019020999 W JP 2019020999W WO 2020240678 A1 WO2020240678 A1 WO 2020240678A1
Authority
WO
WIPO (PCT)
Prior art keywords
screw
bearing housing
casing
rotor
oil
Prior art date
Application number
PCT/JP2019/020999
Other languages
English (en)
Japanese (ja)
Inventor
直也 光成
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2019/020999 priority Critical patent/WO2020240678A1/fr
Priority to EP19930726.5A priority patent/EP3978759A4/fr
Publication of WO2020240678A1 publication Critical patent/WO2020240678A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • 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
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/102—Adjustment of the interstices between moving and fixed parts of the machine by means other than fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/809—Lubricant sump
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves

Definitions

  • the present invention relates to a screw compressor used for compressing a refrigerant such as a refrigerator.
  • the screw compressor is known as one type of positive displacement compressor, and is used as a component of a refrigerant circuit built in, for example, a refrigerator or the like. ..
  • the screw compressor for example, one screw rotor having a spiral tooth groove and two gate rotors having a plurality of gate rotor teeth that fit into the tooth grooves of the screw rotor are housed inside the casing.
  • Single screw compressors are known. In the single screw compressor, the tooth groove of the screw rotor and the gate rotor tooth portion of the gate rotor are meshed with each other and engaged with each other to form a plurality of compression chambers.
  • One end of the screw rotor in the direction of rotation axis is the suction side of the refrigerant, and the other end is the discharge side.
  • the inside of the casing is divided into a low pressure space provided on the suction side of the compression chamber and a high pressure space provided on the discharge side of the compression chamber.
  • the screw rotor is fixed to the screw shaft that rotates by the drive unit provided inside the casing.
  • One shaft end of the screw shaft is rotatably supported by a bearing housing having a bearing inside, and the other shaft end is connected to a drive unit.
  • the screw compressor when the screw rotor is rotationally driven via the screw shaft rotated by the drive unit, the refrigerant in the low pressure space is sucked into the compression chamber and compressed, and the refrigerant compressed in the compression chamber is discharged into the high pressure space. It is a configuration.
  • some screw compressors are provided with a pair of slide valves arranged in a slide groove formed on the inner cylinder surface of the casing and slidably movable in the direction of the rotation axis of the screw rotor.
  • the slide valve is provided to slide in the direction of the rotation axis of the screw rotor and change the discharge start position of the high-pressure gas refrigerant compressed in the compression chamber to change the discharge opening timing and change the internal volume ratio.
  • This slide valve includes a valve body portion facing the screw rotor and a guide portion forming a sliding surface facing the outer peripheral surface of the bearing housing.
  • the screw rotor may thermally expand due to an increase in the temperature of the refrigerant gas compressed in the compression chamber, and the gap between the outer peripheral surface of the screw rotor and the inner cylinder surface of the casing and the slide valve may decrease. Further, in the screw compressor, after the operation is stopped, the screw rotor may rotate in the reverse direction due to the high and low differential pressure in the casing. When the screw rotor rotates in the reverse direction, the valve body of the slide valve may fall toward the screw rotor or rotate in the circumferential direction due to the influence of changes in the internal pressure of the compression chamber. As a result, a part of the valve body of the slide valve may protrude from the inner peripheral surface of the casing bore and come into contact with the screw rotor, resulting in seizure or the like.
  • Patent Document 1 a protrusion is provided on the guide portion of the slide valve so as to project relative to the valve body in the circumferential direction, and when the slide valve rotates in the circumferential direction, the protrusion is brought into contact with the bearing holder.
  • a structure that avoids contact between the slide valve and the screw rotor is disclosed.
  • the present invention has been made to solve the above problems, and an object of the present invention is to provide a highly reliable screw compressor capable of suppressing contact between a slide valve and a screw rotor. ..
  • the screw compressor according to the present invention has a casing constituting the outer shell, a screw shaft arranged in the casing and driven to rotate, and a spiral tooth groove on the outer peripheral surface, and is fixed to the screw shaft.
  • a gate rotor having a plurality of gate rotor teeth that fit into the tooth grooves of the screw rotor, and forming a compression chamber for compressing a refrigerant together with the casing and the screw rotor, and an inner cylinder surface of the casing. It has a slide valve provided in the formed slide groove and slidably movable in the direction of the rotation axis of the screw rotor, and a bearing that rotatably supports one end of the screw shaft on the outer peripheral surface.
  • the bearing housing that slides the slide valve, the oil separator that separates the oil mixed in the refrigerant compressed in the compression chamber, and the oil that is connected to the oil separator and separated by the oil separator are used.
  • the bearing housing is provided with a heating mechanism that thermally expands the bearing housing in the radial direction during operation.
  • the thermally expanded bearing housing abuts and supports the slide valve before the valve body portion of the slide valve collapses toward the screw rotor side or rotates in the circumferential direction. Contact with the rotor can be suppressed, and a highly reliable screw compressor can be realized.
  • FIG. It is sectional drawing which showed the internal structure of the screw compressor which concerns on Embodiment 1.
  • FIG. It is sectional drawing which shows the internal structure of the screw compressor which concerns on Embodiment 1, and shows the part different from FIG.
  • FIG. It is a perspective view which showed the structure of the bearing housing of the screw compressor which concerns on Embodiment 1.
  • FIG. It is the operation of the compression part of the screw compressor which concerns on Embodiment 1, and is explanatory drawing which showed the suction process.
  • FIG. 1 It is the operation of the compression part of the screw compressor which concerns on Embodiment 1, and is explanatory drawing which showed the compression stroke. It is the operation of the compression part of the screw compressor which concerns on Embodiment 1, and is explanatory drawing which showed the discharge process. It is sectional drawing which showed the internal structure of the screw compressor which concerns on Embodiment 2.
  • FIG. 2 It is a perspective view which showed the structure of the bearing housing of the screw compressor which concerns on Embodiment 2.
  • FIG. 1 is a cross-sectional view showing the internal structure of the screw compressor according to the first embodiment.
  • FIG. 2 is a cross-sectional view showing an internal structure of the screw compressor according to the first embodiment, which is different from FIG.
  • FIG. 3 is an enlarged cross-sectional view showing a main part of the arrow line AA shown in FIG.
  • FIG. 4 is an enlarged cross-sectional view showing a main part of the arrow line BB shown in FIG.
  • FIG. 5 is a perspective view showing the structure of the bearing housing of the screw compressor according to the first embodiment.
  • the screw compressor 100 includes a cylindrical casing 1 constituting an outer shell, a compression unit 2 and a drive unit 3 provided inside the casing 1, and one end of the outside of the casing 1. It is composed of an oil separator 14 provided on the side.
  • the inside of the casing 1 is divided into a low pressure space 10 and a high pressure space 11.
  • the compression unit 2 includes a screw shaft 4, a screw rotor 5 fixed to the screw shaft 4, a pair of gate rotors 6, a gate rotor support (not shown), and a pair.
  • the slide valve 7 and the bearing housing 8 which has a bearing 80 that rotatably supports the end of the screw shaft 4 and slides the slide valve 7 on the outer peripheral surface thereof are provided.
  • the compression unit 2 is connected to the oil separator 14, and the oil separated by the oil separator 14 is used during operation as shown in FIG.
  • a heating mechanism 9 for thermally expanding the bearing housing 8 in the radial direction is provided.
  • the screw shaft 4 is arranged in the casing 1 and is rotationally driven by the drive unit 3.
  • the screw shaft 4 extends in the pipe axis direction of the casing 1, one shaft end is rotatably supported by a bearing 80 arranged to face the discharge side of the screw rotor 5, and the other shaft end is supported. It is connected to the drive unit 3.
  • the screw rotor 5 has a plurality of spiral tooth grooves 5a on the outer peripheral surface of the cylindrical body.
  • the screw rotor 5 is fixed to the screw shaft 4 and rotates together with the screw shaft 4 rotated by the drive unit 3.
  • the low pressure space 10 side in the rotation axis direction is the refrigerant suction side
  • the high pressure space 11 end is the discharge side.
  • the screw rotor 5 has a predetermined gap S formed between the screw rotor 5 and the slide valve 7. This is to prevent, for example, contact when assembling the screw compressor 100, or contact between the slide valve 7 and the screw rotor 5 during operation of the screw compressor 100 to cause seizure or the like.
  • a plurality of gate rotor tooth portions 6a that fit into the tooth grooves 5a of the screw rotor 5 are formed on the outer peripheral portion, and as shown in FIGS. 1 and 2, the screw rotor 5 is sandwiched in the radial direction. It is located in.
  • the tooth groove 5a of the screw rotor 5 and the gate rotor tooth portion 6a of the gate rotor 6 are meshed with each other and engaged with each other to form a compression chamber 20.
  • the screw compressor 100 has a configuration in which two gate rotors 6 are arranged so as to face each other with a 180 degree shift from one screw rotor 5.
  • the gate rotor support (not shown) has a plurality of gate rotor support teeth provided so as to face the plurality of gate rotor teeth 6a, and supports the gate rotor 6.
  • the slide valve 7 is provided in a slide groove 12 formed on the inner cylinder surface of the casing 1, and is configured to be slidable in the rotation axis direction of the screw rotor 5.
  • the slide valve 7 is an internal volume ratio adjusting valve as an example.
  • the slide valve 7 includes a valve body portion 70 facing the screw rotor 5 and a guide portion 71 having a sliding surface facing the outer peripheral surface of the bearing housing 8.
  • the valve body portion 70 and the guide portion 71 are connected by a connecting portion 72.
  • a discharge port 7a for the refrigerant compressed in the compression chamber 20 is provided between the valve body portion 70 and the guide portion 71. The refrigerant discharged from the discharge port 7a is discharged into the high pressure space 11 through the discharge gas passage.
  • the slide valve 7 is connected to the slide valve drive device 74 via a rod 73 fixed to the end surface of the guide portion 71. That is, the slide valve 7 is moved in parallel with the screw shaft 4 by the rod 73 that operates in the axial direction by driving the slide valve driving device 74.
  • the slide valve drive device 74 has, for example, a gas pressure driven configuration, a hydraulically driven configuration, a motor driven configuration, and the like.
  • the valve body 70 of the slide valve 7 moves in parallel with the screw shaft 4, so that the discharge timing of the refrigerant sucked into the compression chamber 20 is adjusted.
  • the slide valve 7 can be positioned on the suction side to accelerate the opening of the discharge port 7a, thereby accelerating the discharge timing, and move the slide valve 7 to the discharge side to delay the opening of the discharge port 7a. Therefore, the discharge timing can be delayed. That is, the screw compressor 100 operates at a low internal volume ratio when the discharge timing is advanced, and operates at a high internal volume ratio when the discharge timing is delayed.
  • the bearing housing 8 is provided close to the discharge side end of the screw rotor 5.
  • the outer diameter of the bearing housing 8 is formed to be larger than the outer diameter of the screw rotor 5.
  • the bearing housing 8 since the bearing housing 8 must be inserted into the casing 1 at the position where the screw rotor 5 is housed, the bearing housing 8 is formed with an outer diameter smaller than the inner diameter of the casing 1 at that position.
  • the outer diameter of the bearing housing 8 may be smaller than the outer diameter of the screw rotor 5.
  • the oil separator 14 separates the oil 15 mixed in the gas refrigerant compressed in the compression chamber 20.
  • the oil 15 separated by the oil separator 14 is used to lubricate the bearing 80 that supports one end of the screw shaft 4, or to seal the gap between the inner wall surface of the casing 1 and the screw rotor 5. It circulates inside 1.
  • the drive unit 3 is composed of an electric motor 30.
  • the electric motor 30 is composed of a stator 31 which is inscribed and fixed inside the casing 1 and has a gap in the radial direction, and a motor rotor 32 which is rotatably arranged inside the stator 31.
  • the motor rotor 32 is connected to the shaft end of the screw shaft 4 and is arranged on the same axis as the screw rotor 5.
  • the screw compressor 100 rotates the screw rotor 5 by driving the electric motor 30 to rotate the screw shaft 4.
  • the electric motor 30 is of the inverter type, the rotation speed is variably driven by an inverter (not shown), and the screw shaft 4 is operated by accelerating or decelerating the rotation speed.
  • FIG. 6 is an explanatory view showing the operation of the compression unit of the screw compressor according to the first embodiment and showing the suction stroke.
  • FIG. 7 is an explanatory diagram showing the operation of the compression unit of the screw compressor according to the first embodiment and showing the compression stroke.
  • FIG. 8 is an explanatory diagram showing the operation of the compression unit of the screw compressor according to the first embodiment and showing the discharge stroke.
  • each process will be described focusing on the compression chamber 20 shown by the hatching of dots.
  • the screw rotor 5 is rotated by the electric motor 30 via the screw shaft 4, so that the gate rotor tooth portion 6a of the gate rotor 6 constitutes the compression chamber 20. It moves relatively in the tooth groove 5a.
  • the suction stroke (FIG. 6), the compression stroke (FIG. 7), and the discharge stroke (FIG. 8) are set as one cycle, and this cycle is repeated.
  • FIG. 6 shows the state of the compression chamber 20 in the suction stroke.
  • the screw rotor 5 is driven by the electric motor 30 and rotates in the direction of the solid arrow. As a result, the volume of the compression chamber 20 is reduced as shown in FIG.
  • the compression chamber 20 communicates with the discharge port 7a as shown in FIG. As a result, the high-pressure refrigerant gas compressed in the compression chamber 20 is discharged to the outside from the discharge port 7a. Then, the same compression is performed again on the back surface of the screw rotor 5.
  • the screw rotor 5 thermally expands due to the temperature rise of the refrigerant gas compressed in the compression chamber 20, and the gap S between the outer peripheral surface of the screw rotor 5 and the inner cylinder surface of the casing 1 and the slide valve 7 May decrease.
  • the screw rotor 5 may rotate in the reverse direction due to the high / low differential pressure in the casing 1 after the operation is stopped, and when the screw rotor 5 rotates in the reverse direction, the internal pressure of the compression chamber 20 may change.
  • the valve body 70 of the slide valve 7 may fall toward the screw rotor 5 or rotate in the circumferential direction. As a result, a part of the valve body portion 70 of the slide valve 7 may protrude and come into contact with the screw rotor 5 to cause seizure or the like.
  • the screw compressor 100 is connected to the oil separator 14 and uses the oil separated by the oil separator 14.
  • a heating mechanism 9 that thermally expands the bearing housing 8 in the radial direction during operation is provided.
  • the heating mechanism 9 includes an oil passage 90 formed in the wall of the casing 1 facing the bearing housing 8 and connected to the oil separator 14, a groove 91 formed in the bearing housing 8 and communicating with the oil passage 90, and the like. have. That is, the heating mechanism 9 has a configuration in which high-temperature and high-pressure oil separated by the oil separator 14 is circulated to the groove 91 through the oil passage 90, and the bearing housing 8 is thermally expanded in the radial direction during operation.
  • the groove 91 is formed along the circumferential direction of the bearing housing 8.
  • the groove 91 in the first embodiment shown in FIG. 5 is composed of a first groove 91a and a second groove 91b in which two bearing housings 8 are arranged in parallel at intervals in the pipe axis direction.
  • One end of the first groove portion 91a is a suction port 91c connected to the oil passage 90, and the other end is connected to the second groove portion 91b.
  • One end of the second groove portion 91b is connected to the first groove portion 91a, and the other end is a discharge port 91d connected to the compression chamber 20.
  • the discharge port 91d and the compression chamber 20 are connected by an oil communication passage 90a formed in the wall of the casing 1.
  • the high-temperature and high-pressure oil that has flowed into the groove 91 of the bearing housing 8 circulates due to the differential pressure in the casing 1 and is supplied to the tooth groove 5a of the screw rotor 5, the bearing 80, and the like.
  • the bearing housing 8 is thermally expanded before the valve body 70 of the slide valve 7 collapses toward the screw rotor 5 or rotates in the circumferential direction. Is in contact with and supports the guide portion 71 of the slide valve 7, so that contact between the slide valve 7 and the screw rotor 5 can be suppressed, and a highly reliable screw compressor can be realized.
  • the bearing housing 8 having the groove 91 formed on the outer peripheral portion is formed in advance by using a mold, and the surface is processed by using a lathe processing machine. Since the surface of the groove 91 does not affect the function of the screw compressor 100, there is no problem even if the cast surface 92 remains. Therefore, the surface of the groove 91 remains the cast surface 92 formed by the mold. That is, by leaving the groove 91 in the screw compressor 100 according to the first embodiment as the cast surface 92, additional processing of the groove 91 becomes unnecessary, the manufacturing cost can be suppressed, and the productivity can be improved. Can be done.
  • a spacer 13 is provided on the inner wall surface of the casing 1 at a position facing the bearing housing 8 with the screw rotor 5 interposed therebetween.
  • the heating mechanism 9 has a branch passage 90b that branches from the oil passage 90, extends in the pipe axis direction of the casing 1, and is connected to the spacer 13. That is, the heating mechanism 9 circulates the high-temperature and high-pressure oil separated by the oil separator 14 to the branch passage 90b through the oil passage 90 to increase the heat transfer area and thermally expand the inner wall surface of the casing 1. Can be done. Therefore, the screw compressor 100 according to the first embodiment can effectively suppress the contact between the casing 1 and the screw rotor 5.
  • the screw compressor 100 does not necessarily have to be provided with a spacer 13 to connect the branch passage 90b branched from the oil passage 90, and the spacer 13 and the branch path may be omitted.
  • the screw compressor 100 has a casing 1 constituting the outer shell, a screw shaft 4 arranged in the casing 1 and driven to rotate, and a spiral tooth groove on the outer peripheral surface. It has 5a and includes a screw rotor 5 fixed to a screw shaft 4. Further, the screw compressor 100 has a plurality of gate rotor tooth portions 6a that fit into the tooth grooves 5a of the screw rotor 5, and together with the casing 1 and the screw rotor 5 form a compression chamber 20 that compresses the refrigerant.
  • a slide valve 7 is provided in a slide groove 12 formed on the inner cylinder surface of the casing 1 so as to be slidable in the direction of the rotation axis of the screw rotor 5.
  • the screw compressor 100 includes a bearing housing 8 having a bearing 80 that rotatably supports one end of the screw shaft 4, and an oil separator 14 that separates oil mixed in the refrigerant compressed in the compression chamber 20. And a heating mechanism 9 which is connected to the oil separator 14 and uses the oil separated by the oil separator 14 to thermally expand the bearing housing 8 in the radial direction during operation.
  • the heating mechanism 9 includes an oil passage 90 formed in the wall of the casing 1 facing the bearing housing 8 and connected to the oil separator 14, a groove 91 formed in the bearing housing 8 and communicating with the oil passage 90, and the like. have.
  • the heating mechanism 9 has a configuration in which high-temperature and high-pressure oil separated by the oil separator 14 is circulated to the groove 91 through the oil passage 90, and the bearing housing 8 is thermally expanded in the radial direction during operation.
  • the thermally expanded bearing housing 8 of the slide valve 7 is formed before the valve body 70 of the slide valve 7 collapses toward the screw rotor 5 or rotates in the circumferential direction. Since it abuts and supports the guide portion 71, contact between the slide valve 7 and the screw rotor 5 can be suppressed, and a highly reliable screw compressor can be realized.
  • the heating mechanism 9 has a branch passage 90b that branches from the oil passage 90, extends in the pipe axis direction of the casing 1, and is connected to the spacer 13. That is, the heating mechanism 9 circulates the high-temperature and high-pressure oil separated by the oil separator 14 to the branch passage 90b through the oil passage 90 to increase the heat transfer area and thermally expand the inner wall surface of the casing 1. Can be done. Therefore, the screw compressor 100 according to the first embodiment can effectively suppress the contact between the casing 1 and the screw rotor 5.
  • the groove 91 is a cast surface 92 formed by a mold. That is, in the screw compressor 100 according to the first embodiment, by leaving the surface of the groove 91 that does not affect the function as the cast surface 92, additional processing of the groove 91 becomes unnecessary and the manufacturing cost is suppressed. Can increase productivity.
  • FIG. 9 is a cross-sectional view showing the internal structure of the screw compressor according to the second embodiment.
  • FIG. 10 is a perspective view showing the structure of the bearing housing of the screw compressor according to the second embodiment.
  • the same components as those of the screw compressor 100 described in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted as appropriate.
  • the groove 91 of the heating mechanism 9 is formed to a position facing the outer peripheral surface of the guide portion 71 of the slide valve 7. .. That is, the high-temperature and high-pressure oil separated by the oil separator 14 is circulated to the groove 91 through the oil passage 90 to thermally expand the bearing housing 8 in the radial direction during operation, and the guide portion 71 of the slide valve 7. The outer peripheral surface is expanded.
  • the branch passage 90c branched from the oil passage 90 is connected to the compression chamber 20.
  • the high-temperature and high-pressure oil that has flowed into the oil passage 90 circulates at the differential pressure in the casing 1 and is supplied to the tooth groove 5a of the screw rotor 5, the bearing 80, or the like.
  • the screw compressor 101 thermally expands with the thermally expanded bearing housing 8 before the valve body 70 of the slide valve 7 collapses toward the screw rotor 5 or rotates in the circumferential direction. Since the guide portion 71 of the slide valve 7 comes into contact with each other, the contact between the slide valve 7 and the screw rotor 5 can be effectively suppressed, and a highly reliable screw compressor can be realized.
  • the screw compressor 101 also has a spacer 13 provided on the inner wall surface of the casing 1 located between the compression unit 2 and the drive unit 3.
  • a branch passage 90b branched from the oil passage 90 may be connected to the seat 13.
  • FIG. 11 is a cross-sectional view showing the internal structure of the screw compressor according to the third embodiment.
  • the same components as those of the screw compressor 100 described in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted as appropriate.
  • the groove 91 is formed along the pipe axis direction of the bearing housing 8. That is, the heating mechanism 9 has a configuration in which high-temperature and high-pressure oil is circulated from the oil separator 14 through the oil passage 90 to the groove 91, and the entire surface of the bearing housing 8 is thermally expanded in the radial direction during operation. As shown in FIG. 11, a plurality of groove portions 91 formed along the pipe axis direction may be formed in parallel in the circumferential direction, or may be formed by one groove portion 91.
  • the branch passage 90d branched from the oil passage 90 is connected to the compression chamber 20.
  • the high-temperature and high-pressure oil that has flowed into the oil passage 90 circulates at the differential pressure in the casing 1 and is supplied to the tooth groove 5a of the screw rotor 5, the bearing 80, or the like.
  • the thermally expanded bearing housing 8 becomes the slide valve 7 before the valve body 70 of the slide valve 7 collapses toward the screw rotor 5 or rotates in the circumferential direction. Since it abuts and supports, the contact between the slide valve 7 and the screw rotor 5 can be suppressed, and a highly reliable screw compressor can be realized.
  • the screw compressor 102 also has a spacer 13 provided on the inner wall surface of the casing 1 located between the compression unit 2 and the drive unit 3.
  • a branch passage 90b branched from the oil passage 90 may be connected to the seat 13.
  • the screw compressor 100 has been described above based on the embodiment, the screw compressor 100 is not limited to the configuration of the above-described embodiment.
  • the internal configuration of the screw compressor 100 is not limited to the above-mentioned contents, and may include other components.
  • the screw compressor 100 has been described by taking a single-stage single screw compressor as an example, but for example, a two-stage single screw compressor may be used.
  • the slide valve 7 is not limited to the internal volume ratio adjusting valve, and may be configured to adjust the compression capacity, for example.
  • the gate rotor 6 is not limited to the two configurations shown in the figure, and may be one.
  • the screw compressor 100 includes a range of design changes and application variations normally performed by those skilled in the art within a range that does not deviate from the technical idea thereof.

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

Abstract

La présente invention concerne un compresseur à vis pourvu : d'un carter formant un extérieur ; d'un arbre à vis entraîné en rotation ; d'un rotor à vis fixé à l'arbre à vis ; d'un rotor de porte formant, conjointement avec le carter et le rotor à vis, une chambre de compression pour comprimer un fluide frigorigène ; d'un distributeur à tiroir conçu pour être libre de coulisser dans la direction de l'axe de rotation du rotor à vis ; d'un logement de palier comprenant en son sein un palier pour supporter une extrémité de l'arbre à vis avec une liberté de rotation ; d'un séparateur d'huile pour séparer l'huile mélangée dans le fluide frigorigène qui a été comprimé dans la chambre de compression ; et d'un mécanisme de chauffage qui est raccordé au séparateur d'huile et qui utilise l'huile séparée dans le séparateur d'huile pour amener le logement de palier à subir une dilatation thermique dans la direction radiale pendant le fonctionnement.
PCT/JP2019/020999 2019-05-28 2019-05-28 Compresseur à vis WO2020240678A1 (fr)

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PCT/JP2019/020999 WO2020240678A1 (fr) 2019-05-28 2019-05-28 Compresseur à vis
EP19930726.5A EP3978759A4 (fr) 2019-05-28 2019-05-28 Compresseur à vis

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PCT/JP2019/020999 WO2020240678A1 (fr) 2019-05-28 2019-05-28 Compresseur à vis

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024075275A1 (fr) * 2022-10-07 2024-04-11 三菱電機株式会社 Compresseur à vis

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115076107B (zh) * 2022-07-06 2023-06-23 杭州千岛泵业有限公司 一种悬臂立式螺杆真空泵

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Publication number Priority date Publication date Assignee Title
JPH05106572A (ja) * 1991-10-17 1993-04-27 Daikin Ind Ltd 一軸形スクリユー圧縮機
JP2013060877A (ja) 2011-09-13 2013-04-04 Daikin Industries Ltd スクリュー圧縮機
JP2019019678A (ja) * 2017-07-11 2019-02-07 ダイキン工業株式会社 スクリュー圧縮機
JP2019019682A (ja) * 2017-07-12 2019-02-07 ダイキン工業株式会社 スクリュー圧縮機

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010106787A1 (fr) * 2009-03-16 2010-09-23 ダイキン工業株式会社 Compresseur à vis
JP2013253543A (ja) * 2012-06-06 2013-12-19 Daikin Industries Ltd スクリュー圧縮機

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Publication number Priority date Publication date Assignee Title
JPH05106572A (ja) * 1991-10-17 1993-04-27 Daikin Ind Ltd 一軸形スクリユー圧縮機
JP2013060877A (ja) 2011-09-13 2013-04-04 Daikin Industries Ltd スクリュー圧縮機
JP2019019678A (ja) * 2017-07-11 2019-02-07 ダイキン工業株式会社 スクリュー圧縮機
JP2019019682A (ja) * 2017-07-12 2019-02-07 ダイキン工業株式会社 スクリュー圧縮機

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Title
See also references of EP3978759A4

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024075275A1 (fr) * 2022-10-07 2024-04-11 三菱電機株式会社 Compresseur à vis

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EP3978759A1 (fr) 2022-04-06
EP3978759A4 (fr) 2022-07-06

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