WO2019102615A1 - Compresseur à vis unique et dispositif à cycle de réfrigération comprenant ledit compresseur à vis unique - Google Patents

Compresseur à vis unique et dispositif à cycle de réfrigération comprenant ledit compresseur à vis unique Download PDF

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Publication number
WO2019102615A1
WO2019102615A1 PCT/JP2017/042387 JP2017042387W WO2019102615A1 WO 2019102615 A1 WO2019102615 A1 WO 2019102615A1 JP 2017042387 W JP2017042387 W JP 2017042387W WO 2019102615 A1 WO2019102615 A1 WO 2019102615A1
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WO
WIPO (PCT)
Prior art keywords
gate rotor
single screw
screw compressor
rotor
gate
Prior art date
Application number
PCT/JP2017/042387
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English (en)
Japanese (ja)
Inventor
栗田　慎
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 JP2019556074A priority Critical patent/JP6800348B2/ja
Priority to PCT/JP2017/042387 priority patent/WO2019102615A1/fr
Priority to TW107114226A priority patent/TWI660122B/zh
Publication of WO2019102615A1 publication Critical patent/WO2019102615A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/48—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

Definitions

  • the screw rotor is accommodated in the casing, and the teeth of the disc-shaped gate rotor are engaged with the screw grooves formed on the outer peripheral surface of the screw rotor, thereby forming a compression chamber in the casing.
  • a refrigeration cycle apparatus equipped with the single screw compressor.
  • the gate rotor is engaged with the screw rotor in a state of being fixed to and supported by the gate rotor support.
  • Various fixing structures for the gate rotor and the gate rotor support have been proposed.
  • the shaft portion of the screw rotor support is inserted into the through hole formed in the central portion of the gate rotor, and the gate rotor Pins are inserted into pin holes provided in communication with the gate rotor support to fix the gate rotor and the gate rotor support.
  • the gate rotor is made of resin, and the gate rotor support is made of iron, and the gate rotor is fixedly supported on the base of the gate rotor support.
  • the rotation shaft provided integrally with the screw rotor is positively rotated by the motor, whereby the screw rotor is positively rotated.
  • the screw rotor rotates forward, the refrigerant is sucked into the compression chamber from the low pressure space in the casing as the screw rotor rotates.
  • the volume of the compression chamber is reduced as the teeth of the gate rotor move in the screw groove, and the refrigerant in the compression chamber is compressed. Then, the compressed refrigerant is discharged from the compression chamber to the high pressure space in the casing.
  • the pressure in the compression chamber always acts on the upper surface of the gate rotor during operation and the lower surface of the gate rotor Low pressure space pressure always acts.
  • the gate rotor is supported by the pedestal of the gate rotor support, the tip of the tooth of the gate rotor protrudes outward beyond the pedestal of the gate rotor support, and a low pressure space is formed on the lower surface of this projection. Internal pressure acts.
  • a force in the direction from the upper surface to the lower surface acts on the teeth of the gate rotor, and during operation, the teeth of the gate rotor move to the gate rotor support side by the pressure difference between the compression chamber and the low pressure space. It is pressed.
  • the present invention has been made in view of such a point, and provides a single screw compressor capable of preventing fatigue failure of the gate rotor at the time of reverse rotation of the screw rotor generated at the time of operation stop, and the single screw compressor
  • An object of the present invention is to provide a provided refrigeration cycle apparatus.
  • a single screw compressor comprises a screw rotor having a plurality of screw grooves formed on the outer peripheral surface, and a disk-shaped gate rotor having a plurality of tooth portions engaged with the plurality of screw grooves on the outer peripheral portion.
  • a single screw compressor comprising: a gate rotor support having contact surfaces in contact with a plurality of teeth of the gate rotor, wherein the gate rotor and the gate rotor support rotate to compress the refrigerant as the screw rotor rotates.
  • a fixing portion is provided for fixing the tooth portion of the gate rotor and the gate rotor support, and the fixing portion is formed on the fitting portion provided on the tooth portion of the gate rotor and the contact surface of the gate rotor support.
  • the linear expansion coefficient of the fitting portion is larger than the linear expansion coefficient of the gate rotor support, and the fitting based on the temperature rise during operation Fitting portion due to thermal expansion of the parts is intended to fit in contact with the recess.
  • the fitting portion provided on the tooth portion of the gate rotor is thermally expanded during operation and fitted in the recess provided on the gate rotor support, thereby fixing the tooth portion of the gate rotor to the gate rotor support It was set up. For this reason, even if reverse rotation of the screw rotor occurs at the time of operation stop, deformation of the teeth of the gate rotor can be suppressed, and fatigue failure of the gate rotor can be prevented.
  • the screw rotor is one single-stage single-screw compressor, and an example is a twin gate rotor system in which two gate rotors are engaged with one screw rotor and two compression chambers are formed. The form will be described.
  • FIG. 1 is a schematic cross-sectional view of a main structure of a single screw compressor according to Embodiment 1 of the present invention.
  • FIG. 2 is a schematic longitudinal sectional view of a single screw compressor according to Embodiment 1 of the present invention.
  • the single screw compressor includes a casing 1, a screw rotor 2, an electric motor 7, and a rotating shaft 8 fixed to the electric motor 7 and rotationally driven by the electric motor 7.
  • the casing 1 is formed in a tubular shape, and the screw rotor 2 is rotatably accommodated in the casing 1.
  • the screw rotor 2 has a cylindrical shape, and a plurality of screw grooves 2 a spirally extending from one end side to the other end side of the screw rotor 2 are formed on the outer peripheral portion.
  • One end of the screw rotor 2 is a suction side of the refrigerant, and the other end is a discharge side of the refrigerant.
  • the inside of the casing 1 is separated by a partition (not shown) into a low pressure space 20 filled with a low pressure refrigerant and a high pressure space filled with a high pressure refrigerant, one end of the screw rotor 2 communicates with the low pressure space 20 The end side communicates with the high pressure space. Further, at the center of the screw rotor 2, a rotation shaft 8 is provided integrally with the rotation.
  • each gate rotor support chamber 21 is formed to face each other with the central axis 13 of the screw rotor 2 as a center.
  • a gate rotor 3 and a gate rotor support 4 for supporting the gate rotor 3 are accommodated in each gate rotor support chamber 21.
  • the gate rotor 3 and the gate rotor support 4 accommodated in each gate rotor support chamber 21 are arranged to be rotated by 180 ° around the central axis 13 of the screw rotor 2.
  • the gate rotor support 4 is rotatably supported by a bearing 9a and a bearing 9b which are disposed such that the central axis 14 thereof is substantially perpendicular to the central axis 13 of the screw rotor 2 and spaced apart in the direction of the central axis 14 It is done.
  • the gate rotor 3 has a disk shape, and has a plurality of teeth 30 on the outer periphery, and the teeth 30 are engaged with the screw groove 2 a of the screw rotor 2.
  • the compression chamber 10 is formed in a space surrounded by the screw groove 2 a, the tooth portion 30 of the gate rotor 3 and the inner peripheral surface of the casing 1.
  • two compression chambers 10 are formed, and each compression chamber 10 has a positional relationship facing the central axis 13 of the screw rotor 2 by 180 °.
  • two slide grooves 11 extending in the rotational axis 8 direction are formed on the inner wall surface of the casing 1. These two slide grooves 11 are arranged to be rotated 180 ° around the rotation shaft 8.
  • a rod-like internal volume ratio variable valve 12 having a crescent-shaped cross section is accommodated slidably.
  • a rod 15 connected to a linear actuator (not shown) is fixed to one end face of the variable volume valve 12 in the sliding direction, and the variable volume valve is driven by driving the linear actuator. 12 move in the slide groove 11.
  • the discharge timing of the refrigerant sucked into the compression chamber 10 can be adjusted.
  • the position of the internal volume ratio variable valve 12 is controlled in order to adjust the discharge timing so as to increase the energy efficiency.
  • the motor 7 is composed of a stator 5 fixed inward in the casing 1 and a rotor 6 disposed inside the stator 5.
  • the rotor 6 is fixed to the rotating shaft 8 in the same manner as the screw rotor 2 and is arranged coaxially with the screw rotor 2. Then, when the motor 7 is driven, the rotary shaft 8 rotates and the screw rotor 2 rotates forward.
  • the motor 7 is configured to be able to adjust the rotational speed of the rotating shaft 8 using an inverter (not shown). Thereby, the single screw compressor can adjust the rotational speed of the motor 7 to change the operating capacity.
  • the motor 7 is not limited to one having a variable rotational speed by an inverter, and may have a constant speed.
  • the first embodiment is characterized in that a fixing portion 50 (see FIG. 2) for fixing the tooth portion 30 of the gate rotor 3 and the gate rotor support 4 is provided. Further, by providing the fixing portion 50, it is possible to prevent fatigue failure of the gate rotor 3 due to bending and deformation of the tooth portion 30 of the gate rotor 3 at the time of operation stop.
  • the fixing portion 50 is made of different materials of the gate rotor 3 and the gate rotor support 4 and is fixed to each other by utilizing thermal expansion during operation due to the difference in linear expansion coefficient. That is, during operation, the gas sucked into the compression chamber 10 is compressed to increase the temperature. Therefore, as the temperature rises, the temperatures of the gate rotor 3 and the gate rotor support 4 also rise above the normal temperature during stoppage. Due to this temperature rise, the gate rotor 3 and the gate rotor support 4 thermally expand.
  • the structures of the gate rotor 3 and the gate rotor support 4 will be described with reference to FIGS. 3 to 6, and the fixing portion 50 will be described subsequently to the description.
  • FIG. 3 is a view showing a gate rotor of the single screw compressor according to Embodiment 1 of the present invention, where (a) is a plan view and (b) is a cross-sectional view taken along the line AA of (a).
  • FIG. 4 is a view showing a gate rotor support of the single screw compressor according to Embodiment 1 of the present invention, where (a) is a plan view and (b) is a cross-sectional view taken along line AA of (a).
  • FIG. 5 is an enlarged cross-sectional view before expansion of the fixed portion of the gate rotor and the gate rotor support, which is a main part of the single screw compressor according to Embodiment 1 of the present invention.
  • the gate rotor 3 has a disk shape, has a plurality of teeth 30 on the outer peripheral surface, and has a through hole 31 at the center. Further, through holes 32 are formed in each of the teeth 30. The through holes 32 are formed outside the diameter R of a circle connecting the roots of the respective tooth portions 30 of the gate rotor 3.
  • FIG. 3 shows an example in which there are eleven tooth portions 30 of the gate rotor 3 and the through holes 32 are provided in all the tooth portions 30 of the gate rotor 3, the number may not necessarily be all.
  • the pins 60 are press-fit into the through holes 32 from the lower surface side of the gate rotor 3.
  • the pin 60 is made of the same material as the gate rotor 3 and has a structure in which the shaft 61 and a cylindrical head 62 larger in diameter than the shaft 61 are integrally formed, and the shaft 61 is a through hole 32. And is fixed to the teeth 30.
  • the gate rotor support 4 has a substantially disc-like pedestal portion 40 having a planar contact surface 40 a on which the gate rotor 3 is disposed, and a shaft portion 41 extending from both surfaces of the pedestal portion 40 in the central axis direction of the pedestal portion 40. And an axial portion 42.
  • the pedestal portion 40 has the same number of tooth portions 43 corresponding to the tooth portions 30 of the gate rotor 3 on the outer peripheral portion.
  • a cylindrical recess 44 into which the head 62 of the pin 60 is inserted is formed in a portion of the contact surface 40 a that constitutes the tooth portion 43.
  • the shaft portion 42 of the gate rotor support 4 is inserted into and fitted to the through hole 31 of the gate rotor 3 as shown in FIG.
  • the gate rotor 3 is supported in contact.
  • the gate rotor support 4 is made of an iron material, and by supporting the gate rotor 3 in contact with the pedestal portion 40, the rigidity of the gate rotor 3 made of resin is compensated.
  • the head 62 of the pin 60 fixed to the gate rotor 3 is inserted into the recess 44.
  • the pin 60 and the recess 44 are processed such that their central axes coincide with each other when the head 62 of the pin 60 is inserted into the recess 44, and the head 62 of the pin 60 is in the recess 44. Between the peripheral surface, it is inserted with a uniform gap in the radial direction.
  • the head 62 of the pin 60 corresponds to an example of the “fitting portion”.
  • the fixing portion 50 is configured by the head portion 62 of the pin 60 and the concave portion 44.
  • a pressing member (not shown) is attached to the gate rotor support 4 for pressing the gate rotor 3 from the upper surface side to the lower surface side at the periphery of the through hole 31.
  • the movement in the thickness direction of the gate rotor 3 on the gate rotor support 4 is restrained by the pressing member.
  • movement of the gate rotor 3 in the circumferential direction is also restrained by the fixing portion 50 on the gate rotor support 4, this point will be described later.
  • thermal expansion of the head 62 of the pin 60 during operation is allowed, and the outer peripheral surface of the head 62 of the pin 60 after expansion is in contact with the inner peripheral surface of the recess 44.
  • the height of the head 62 of the pin 60 is designed so that the tip end surface 62a of the head 62 of the pin 60 does not contact the bottom surface 44a of the recess 44 when the head 62 of the pin 60 thermally expands during operation. It is done.
  • the outer diameter ⁇ a of the head portion 62 of the pin 60 is formed larger than the inner diameter ⁇ c of the through hole 32. Assuming that the outer diameter ⁇ a of the head portion 62 of the pin 60 is the same as the inner diameter ⁇ c of the through hole 32, the outer diameter ⁇ a of the head portion 62 is smaller than in the case where it is larger than ⁇ c. It is necessary to make the inner diameter ⁇ b of H smaller than that in FIG. That is, in order to cause the head 62 of the pin 60 to thermally expand and contact the recess 44 during operation, it is necessary to reduce the inner diameter ⁇ b of the recess 44.
  • the head 62 of the pin 60 engages with the step between the recess 44 and the through hole 32 when the pin 60 is fitted to the gate rotor 3, so that the pin 60 can be easily positioned. Becomes easier.
  • the toothed portion 30 and the toothed portion 43 of the assembly of the gate rotor 3 and the gate rotor support 4 are engaged with the screw groove 2a of the screw rotor 2 of iron material as described above.
  • the outer diameter of the toothed portion 43 of the gate rotor support 4 is smaller than the outer diameter of the toothed portion 30 of the gate rotor 3 in order to avoid metal-to-metal contact when the toothed portion 30 and the toothed portion 43 mesh with the screw groove 2a. It is formed. As a result, the tip end of the tooth portion 30 of the resin-made gate rotor 3 comes into contact with the screw groove 2a of the iron material, and metal contact can be avoided.
  • FIG. 6 is an enlarged cross-sectional view after expansion of the fixing portion between the gate rotor and the gate rotor support, which is a main part of the single screw compressor according to Embodiment 1 of the present invention.
  • the head 62 of the pin 60 made of a resin material expands in the recess 44 by the temperature rise (T2-T1) [° C.] from the temperature T1 [° C.] during stop to the temperature T2 [° C.] during operation Do.
  • the gate rotor support 4 made of an iron material also has a temperature rise higher than that during stoppage during operation, but the linear expansion coefficient of the resin material constituting the gate rotor is the linear expansion of the iron material constituting the gate rotor support 4 About twice as large as the coefficient.
  • the head portion 62 of the pin 60 expands and contacts the inner circumferential surface of the recess 44 as shown in FIG.
  • the contact pressure acts as a holding force for the gate rotor 3 so that the teeth 30 of the gate rotor 3 can be fixed to the gate rotor support 4 during operation.
  • This phenomenon occurs at the head 62 of all the pins 60 and the recess 44 of the gate rotor support 4.
  • the tooth portion 30 of the gate rotor 3 is fixed to the gate rotor support 4 by the fixing portion 50, whereby movement of the tooth portion 30 in the axial direction and the circumferential direction is restrained.
  • the motor 7 driving the single screw compressor is activated upon receiving an electrical input from an inverter (not shown).
  • the screw rotor 2 rotates as the rotary shaft 8 rotates, and the refrigerant is sucked into the compression chambers 10.
  • the gate rotor 3 also rotates with the rotation of the screw rotor 2, and after the suction of the refrigerant into the compression chamber 10 is completed, the volume of the compression chamber 10 is reduced and the pressure of the refrigerant drawn into the compression chamber 10 gradually increases.
  • the refrigerant whose pressure has risen is discharged from the compression chamber 10 to the high pressure space through the discharge port (not shown) provided in the casing, and is discharged out of the machine.
  • the timing at which the refrigerant in each compression chamber 10 is discharged from the discharge port (not shown) is adjusted by the internal volume ratio variable valve 12.
  • the pins 60 fixed to the gate rotor 3 thermally expand during operation, and the head portion 62 contacts the inner peripheral surface of the recess 44 of the gate rotor support 4.
  • a fixing portion 50 is provided to fix the tooth portion 30 to the gate rotor support 4. For this reason, it is possible to prevent the tooth portion 30 of the gate rotor 3 from being bent in the upper surface direction during reverse rotation. Therefore, excessive stress is not generated at the root of the tooth portion 30, and fatigue failure of the gate rotor 3 can be prevented.
  • the pin 60 can be more easily positioned on the gate rotor 3 than in the case where the outer diameter ⁇ a of the head portion 62 is the same diameter as the inner diameter ⁇ c of the through hole 32, and the assembly performance can be improved. Further, since the contact pressure at the time of operation can be increased as the outer diameter ⁇ a of the head portion 62 is larger, the gate rotor 3 and the gate rotor support 4 can be firmly fixed.
  • the pin 60 has the shaft portion 61 and the head portion 62 having a diameter larger than that of the shaft portion 61 has been described as an example, but the present invention is not necessarily limited to this configuration.
  • the pin may be configured to have the same diameter from one end to the other end, or the portion inserted into the through hole 32 may be a pin larger in diameter than the portion inserted into the recess 44.
  • the toothed portion 30 of the gate rotor 3 when the toothed portion 30 of the gate rotor 3 is deformed so as to bend in the upper surface direction, the toothed portion 30 contacts a portion called lip surface in the casing 1 and wears. Then, as this wear progresses, the lip gap between the upper surface of the gate rotor 3 and the lip surface is enlarged, which causes the internal leakage of the refrigerant, and causes the insufficient refrigeration capacity.
  • the provision of the fixing portion 50 can prevent the bending of the tooth portion 30. Therefore, the wear in the thickness direction of the tooth portion 30 can be reduced, and the shortage of refrigeration capacity during operation can be prevented.
  • Second Embodiment The second embodiment is different from the first embodiment in the configuration of the fixing unit 50. In the following, only differences from the first embodiment will be described for the second embodiment.
  • FIG. 7 is a view showing a gate rotor of the single screw compressor according to Embodiment 1 of the present invention, where (a) is a plan view and (b) is a cross-sectional view taken along line AA of (a).
  • FIG. 8 is an enlarged cross-sectional view before expansion of a fixed portion of a gate rotor and a gate rotor support, which is a main part of a single screw compressor according to a second embodiment of the present invention.
  • the pin 60 is fixed to the gate rotor 3.
  • the second embodiment has a structure in which the gate rotor 3 and the pin 60 are integrated with a resin of the same material. This structure can be said to have a configuration in which a projection 33 that protrudes to the gate rotor support 4 side is provided on the lower surface of the gate rotor 3.
  • the protrusions 33 correspond to an example of the “fitting portion”.
  • FIG. 9 is an enlarged cross-sectional view after expansion of a fixed portion of a gate rotor and a gate rotor support, which is a main part of a single screw compressor according to a second embodiment of the present invention.
  • the protrusions 33 thermally expand during operation to contact the inner peripheral surface of the recess 44 of the gate rotor support 4, and a contact pressure is generated as in the first embodiment.
  • the contact pressure acts as a holding force for fixing the teeth 30 of the gate rotor 3 to the gate rotor support 4. Therefore, it is possible to prevent the tooth portion 30 of the gate rotor 3 from being bent and deformed in the direction from the lower surface to the upper surface at the time of reverse rotation.
  • the same effect as that of the first embodiment can be obtained, and the assembly of the gate rotor 3 and the pins 60 is not necessary, the assembly process can be simplified, and the cost can be reduced.
  • the third embodiment relates to a refrigeration cycle apparatus provided with the single screw compressor according to the first embodiment or the second embodiment.
  • FIG. 10 is a diagram showing a refrigerant circuit of a refrigeration cycle apparatus according to Embodiment 3 of the present invention.
  • the refrigeration cycle apparatus 70 includes the single screw compressor 71 according to the first embodiment or the second embodiment, a condenser 72, a pressure reducing device 73, and an evaporator 74.
  • the pressure reducing device 73 is constituted by an expansion valve, a capillary tube or the like.
  • the gas refrigerant discharged from the single screw compressor 71 flows into the condenser 72, exchanges heat with the air passing through the condenser 72, and flows out as high-pressure liquid refrigerant. Do.
  • the high pressure liquid refrigerant that has flowed out of the condenser 72 is decompressed by the pressure reducing device 73 to become a low pressure gas-liquid two-phase refrigerant, and flows into the evaporator 74.
  • the low-pressure gas-liquid two-phase refrigerant flowing into the evaporator 74 exchanges heat with the air passing through the evaporator 74 to become a low-pressure gas refrigerant, and is sucked into the single screw compressor 71 again.
  • the refrigeration cycle apparatus 70 configured as described above can suppress the failure of the single screw compressor 71 by providing the single screw compressor 71 according to the first embodiment or the second embodiment, and a highly reliable refrigeration cycle apparatus. It can be done.
  • the components shown in FIG. 10 represent basic components of the refrigeration cycle apparatus, and the refrigeration cycle apparatus of the present invention may be configured to further include components such as liquid reservoirs. .
  • the refrigerating cycle apparatus 70 comprised as mentioned above can be applied to an air conditioner, a refrigerator-freezer, etc.
  • the single screw compressor has been described by way of example of a single screw compressor having a single screw rotor and a twin gate rotor system. It is not limited to this method. It may be a two-stage single screw compressor provided with two screw rotors in the rotational axis direction. Further, a single gate rotor may be engaged with one screw rotor to form a single compression chamber as a single gate rotor type single screw compressor. Even when the present invention is applied to these single screw compressors, the same effects as the present invention can be obtained.

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

Abstract

Compresseur à vis unique pourvu d'une section de fixation destinée à fixer la section dent d'un rotor femelle et d'un support de rotor femelle. La section de fixation est pourvue d'une section d'installation qui est disposée sur la section dent du rotor femelle, et d'un évidement qui est formé dans une surface de contact du support de rotor femelle et dans lequel la section d'installation est installée. Le coefficient de dilatation linéaire de la section d'installation est supérieur à celui du support de rotor femelle, et la dilatation thermique de la section d'installation provoquée par une augmentation de température pendant le fonctionnement amène la section d'installation à entrer en contact avec l'évidement et à être installée dans ce dernier.
PCT/JP2017/042387 2017-11-27 2017-11-27 Compresseur à vis unique et dispositif à cycle de réfrigération comprenant ledit compresseur à vis unique WO2019102615A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2019556074A JP6800348B2 (ja) 2017-11-27 2017-11-27 シングルスクリュー圧縮機及びそのシングルスクリュー圧縮機を備えた冷凍サイクル装置
PCT/JP2017/042387 WO2019102615A1 (fr) 2017-11-27 2017-11-27 Compresseur à vis unique et dispositif à cycle de réfrigération comprenant ledit compresseur à vis unique
TW107114226A TWI660122B (zh) 2017-11-27 2018-04-26 單螺桿壓縮機及包括該單螺桿壓縮機之冷凍循環裝置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2017/042387 WO2019102615A1 (fr) 2017-11-27 2017-11-27 Compresseur à vis unique et dispositif à cycle de réfrigération comprenant ledit compresseur à vis unique

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WO2019102615A1 true WO2019102615A1 (fr) 2019-05-31

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JP7532272B2 (ja) 2021-01-28 2024-08-13 三菱電機ビルソリューションズ株式会社 ボルト着脱治具

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JPS50131113A (fr) * 1974-04-03 1975-10-17
US4227867A (en) * 1978-03-06 1980-10-14 Chicago Pneumatic Tool Company Globoid-worm compressor with single piece housing
JP2009203817A (ja) * 2008-02-26 2009-09-10 Daikin Ind Ltd ゲートロータおよびスクリュー圧縮機
JP2016020644A (ja) * 2014-07-14 2016-02-04 ダイキン工業株式会社 シングルスクリュー圧縮機

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JP4003378B2 (ja) * 2000-06-30 2007-11-07 株式会社日立プラントテクノロジー スクリュー圧縮機
CN201246308Y (zh) * 2008-08-29 2009-05-27 广东正力精密机械有限公司 单螺杆压缩机内星轮转子的轴承机构
JP5126402B2 (ja) * 2010-10-29 2013-01-23 ダイキン工業株式会社 スクリュー圧縮機
CN202673683U (zh) * 2012-07-31 2013-01-16 广东正力精密机械有限公司 一种单螺杆蒸汽压缩机
JP6430003B2 (ja) * 2015-05-26 2018-11-28 三菱電機株式会社 スクリュー圧縮機、及びそのスクリュー圧縮機を備えた冷凍サイクル装置

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Publication number Priority date Publication date Assignee Title
JPS50131113A (fr) * 1974-04-03 1975-10-17
US4227867A (en) * 1978-03-06 1980-10-14 Chicago Pneumatic Tool Company Globoid-worm compressor with single piece housing
JP2009203817A (ja) * 2008-02-26 2009-09-10 Daikin Ind Ltd ゲートロータおよびスクリュー圧縮機
JP2016020644A (ja) * 2014-07-14 2016-02-04 ダイキン工業株式会社 シングルスクリュー圧縮機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7532272B2 (ja) 2021-01-28 2024-08-13 三菱電機ビルソリューションズ株式会社 ボルト着脱治具

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TWI660122B (zh) 2019-05-21
JP6800348B2 (ja) 2020-12-16
TW201925618A (zh) 2019-07-01
JPWO2019102615A1 (ja) 2020-04-09

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