EP3832138B1 - Compresseur à vis - Google Patents

Compresseur à vis Download PDF

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Publication number
EP3832138B1
EP3832138B1 EP18927914.4A EP18927914A EP3832138B1 EP 3832138 B1 EP3832138 B1 EP 3832138B1 EP 18927914 A EP18927914 A EP 18927914A EP 3832138 B1 EP3832138 B1 EP 3832138B1
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EP
European Patent Office
Prior art keywords
screw
rotor
slide valve
casing
screw rotor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP18927914.4A
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German (de)
English (en)
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EP3832138A4 (fr
EP3832138A1 (fr
Inventor
Yu KOBA
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP3832138A4 publication Critical patent/EP3832138A4/fr
Publication of EP3832138A1 publication Critical patent/EP3832138A1/fr
Application granted granted Critical
Publication of EP3832138B1 publication Critical patent/EP3832138B1/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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • 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
    • 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
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw type

Definitions

  • the present invention relates to a screw compressor to be used to compress refrigerant in, for example, a refrigerating machine.
  • a screw compressor has been commonly known as one of the types of positive-displacement compressors.
  • the screw compressor is used as a constituent part of a refrigerant circuit incorporated in a refrigerating machine.
  • a single screw compressor has been commonly known in which, for example, one screw rotor and two gate rotors are accommodated in a casing.
  • the screw rotor includes a tooth groove with a spiral shape.
  • Each of the gate rotors includes a plurality of gate-rotor tooth portions to be fitted in the tooth groove of the screw rotor.
  • the tooth groove of the screw rotor, and the gate-rotor tooth portions of the gate rotors mesh and engage with each other, which forms a plurality of compression chambers.
  • the screw rotor has one end in a rotational-axis direction thereof on the suction side for refrigerant, and has the other end on the discharge side for refrigerant.
  • the interior of the casing is partitioned into a lower-pressure space provided on the suction side of the compression chamber, and a higher-pressure space provided on the discharge side of the compression chamber.
  • the screw rotor is fixed to a screw shaft that is rotated by a drive portion provided in the casing.
  • the screw shaft is supported at one axial end portion rotatably by a bearing housing having a bearing therein, while being connected with the drive portion at the other axial end of the screw shaft.
  • refrigerant in the lower-pressure space is suctioned into the compression chamber and compressed, and then the refrigerant compressed in the compression chamber is discharged to the higher-pressure space.
  • a screw compressor including a pair of slide valves located in a slide groove formed on the inner cylindrical surface of the casing, the pair of slide valves being provided in a slidably movable manner in the rotational-axis direction of the screw rotor.
  • the slide valves are provided to slide in the rotational-axis direction of the screw rotor to change the position at which high-pressure gas refrigerant compressed in the compression chamber starts being discharged, to thereby change the timing of opening the discharge port to change the internal volume ratio.
  • Each of the slide valves includes a valve body portion facing the screw rotor, and a guide portion formed with a sliding surface facing the outer circumferential surface of the bearing housing.
  • the screw rotor may rotate reversely due to a difference between higher pressure and lower pressure in the casing.
  • the screw rotor rotates reversely, there is a possibility that the valve body portion of the slide valve may fall toward the screw rotor or may rotate in the circumferential direction due to a change in internal pressure in the compression chamber and other influences.
  • the valve body portion of the slide valve may fall toward the screw rotor or may rotate in the circumferential direction due to a change in pressure applied from the compression chamber. That is, when the clearance between the slide valve and the screw rotor is excessively small, there is a possibility that the slide valve may contact the screw rotor, and this may cause burning or other problems.
  • Patent Literature 1 discloses a structure in which a step portion is provided on the arc-shaped surface of a slide valve facing a screw rotor, and dynamic pressure of the refrigerant gas sprayed onto the step portion prevents the slide valve from rotating to secure a clearance between the slide valve and the screw rotor.
  • Patent Literature 2 discloses a structure in which a guide portion of a slide valve is provided with a protruding portion protruding in a circumferential direction relative to a valve body portion, and when the slide valve rotates in the circumferential direction, the protruding portion is brought into contact with a bearing holder to avoid the slide valve from contacting the screw rotor.
  • Patent Literature 3 which forms the basis for the preamble of claims 1 and 2, discloses a screw compressor including a drive part for driving the slide valve, and a coupling rod connected to the drive part and the slide valve.
  • the coupling rod is coupled to the slide valve while being biased such that the coupling rod projects from an outer lateral surface of the slide valve.
  • the key factor to secure a clearance between the slide valve and the screw rotor is the dynamic pressure to be applied by fluid. Since the dynamic pressure can vary depending on the operational conditions, it may be difficult to regard the configuration of this invention as reliably securing the clearance. In a case where, for example, the screw rotor rotates reversely when the compressor is stopped, there is a possibility that the dynamic pressure may not be applied to the step portion as intended, and accordingly the clearance between the slide valve and the screw rotor may be reduced more than necessary. As a result of this, the slide valve may contact the screw rotor.
  • the present invention has been made in view of the above problems, and it is an object of the present invention to provide a screw compressor that is reliable and can prevent a slide valve from contacting a screw rotor, while minimizing a decrease in efficiency in the compressor by reducing a clearance between the slide valve and the screw rotor as small as possible.
  • a screw compressor includes: a casing forming an outer shell; a screw shaft located in the casing, the screw shaft being configured to be rotationally driven; a screw rotor fixed to the screw shaft, the screw rotor including a tooth groove with a spiral shape on an outer circumferential surface of the screw rotor; a gate rotor including a plurality of gate-rotor tooth portions to be fitted in the tooth groove of the screw rotor, the gate rotor forming a compression chamber together with the casing and the screw rotor; and a slide valve provided in a slide groove formed on an inner cylindrical surface of the casing, the slide valve being configured to be slidably movable in a rotational-axis direction of the screw rotor, wherein key grooves are formed facing each other on an outer surface of the slide valve and on an inner surface of the casing, respectively, and a key common to the key grooves is inserted in the key grooves, wherein each of the key grooves has a trapezoidal and dovetail
  • a screw compressor includes: a casing forming an outer shell; a screw shaft located in the casing, the screw shaft being configured to be rotationally driven; a screw rotor fixed to the screw shaft, the screw rotor including a tooth groove with a spiral shape on an outer circumferential surface of the screw rotor; a gate rotor including a plurality of gate-rotor tooth portions to be fitted in the tooth groove of the screw rotor, the gate rotor forming a compression chamber together with the casing and the screw rotor; and a slide valve provided in a slide groove formed on an inner cylindrical surface of the casing, the slide valve being configured to be slidably movable in a rotational-axis direction of the screw rotor, wherein a key groove is formed on one of an outer surface of the slide valve and an inner surface of the casing, and a projecting portion to be fitted in the key groove is formed on an other one, wherein the key groove has a trapezoidal and dovetail groove-like shape.
  • the screw compressor can prevent the slide valve from contacting the screw rotor since the slide valve does not rotate in the circumferential direction even when there may be variations in the pressure applied to the inner cylindrical surface of the slide valve, the inner cylindrical surface facing the outer circumferential surface of the screw rotor. Consequently, the screw compressor can be achieved as a reliable screw compressor that can secure a clearance between the slide valve and the screw rotor, while minimizing a decrease in efficiency in the compressor by reducing the clearance between the slide valve and the screw rotor as small as possible.
  • Fig. 1 is a cross-sectional view illustrating an internal structure of a screw compressor according to an embodiment of the present invention.
  • Fig. 2 is a cross-sectional view taken along the line A-A illustrated in Fig. 1 .
  • a screw compressor 100 according to the embodiment, a single-stage single screw compressor will be described as an example.
  • the screw compressor 100 is constituted by a casing 1 having a cylindrical shape and forming an outer shell, a compression portion 2, and a drive portion 3.
  • the compression portion 2 and the drive portion 3 are provided in the casing 1.
  • the interior of the casing 1 is partitioned into a lower-pressure space 10 and a higher-pressure space 11.
  • the compression portion 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 7, a pair of slide valves 8, and a bearing housing 9 having a bearing 90 therein, the bearing 90 rotatably supporting an end portion of the screw shaft 4.
  • the screw shaft 4 extends in the pipe axis direction of the casing 1.
  • the screw shaft 4 is supported at one axial end portion rotatably by the bearing 90 located facing the discharge side of the screw rotor 5, while being connected with the drive portion 3 at the other axial end portion of the screw shaft 4.
  • the screw shaft 4 is rotated by the drive portion 3.
  • the screw rotor 5 includes a plurality of tooth grooves 5a with a spiral shape on the outer circumferential surface of the columnar body of the screw rotor 5.
  • the screw rotor 5 is fixed to the screw shaft 4 and rotates with the screw shaft 4 that is rotated by the drive portion 3.
  • one side of the screw rotor 5 in the rotational-axis direction which is closer to the lower-pressure space 10, is the suction side for refrigerant
  • the other side of the screw rotor 5, which is closer to the higher-pressure space 11 is the discharge side for refrigerant.
  • Each of the gate rotors 6 is formed with a plurality of gate-rotor tooth portions 6a on the outer circumferential portion of the gate rotor 6.
  • the gate-rotor tooth portions 6a are fitted correspondingly in the tooth grooves 5a of the screw rotor 5.
  • the gate rotors 6 are located with the screw rotor 5 interposed between the gate rotors 6 in the radial direction.
  • the tooth grooves 5a of the screw rotor 5, and the gate-rotor tooth portions 6a of the gate rotors 6 mesh and engage with each other, which forms a compression chamber 20.
  • the gate rotor support 7 includes a plurality of gate-rotor-support tooth portions 7a that are provided respectively facing the gaterotor tooth portions 6a.
  • the gate rotor support 7 supports the gate rotor 6.
  • the slide valve 8 is provided in a slide groove 12 formed on the inner cylindrical surface of the casing 1.
  • the slide valve 8 is configured to be slidably movable in the rotational-axis direction of the screw rotor 5.
  • An example of the slide valve 8 is an internal volume-ratio regulating valve.
  • the slide valve 8 includes a valve body portion 80 facing the screw rotor 5, and a guide portion 81 with a sliding surface facing the outer circumferential surface of the bearing housing 9.
  • the valve body portion 80 and the guide portion 81 are connected by a connection portion 82.
  • a discharge port 8a is provided for refrigerant compressed in the compression chamber 20.
  • the refrigerant discharged from the discharge port 8a is then discharged into the higher-pressure space 11 through a discharge gas passage formed on the back side of the guide portion 81.
  • the slide valve 8 is connected to a slide-valve drive device 84 through a rod 83 fixed to an end surface of the guide portion 81. That is, the slide valve 8 moves in a direction parallel to the screw shaft 4 through the rod 83 that operates in the axial direction by driving of the slide-valve drive device 84.
  • the slide-valve drive device 84 is configured to be driven by gas pressure, is configured to be driven by hydraulic pressure, or is configured to be driven by a motor.
  • the valve body portion 80 of the slide valve 8 moves in a direction parallel to the screw shaft 4, so that the timing of discharging refrigerant suctioned into the compression chamber 20 is adjusted.
  • the slide valve 8 is positioned on the suction side to open the discharge port 8a earlier, so that the timing of discharging the refrigerant can be advanced.
  • the slide valve 8 is moved toward the discharge side to delay opening the discharge port 8a, so that the timing of discharging the refrigerant can be delayed. That is, the screw compressor 100 operates at a lower internal volume ratio when the timing of discharging the refrigerant is advanced, and the screw compressor 100 operates at a higher internal volume ratio when the timing of discharging the refrigerant is delayed.
  • the drive portion 3 is constituted by an electric motor 30.
  • the electric motor 30 is in internal contact with the inner portion of the casing 1 and fixed thereto.
  • the electric motor 30 is constituted by a stator 31 and a motor rotor 32.
  • the stator 31 has a clearance in the radial direction.
  • the motor rotor 32 is located on the inner side of the stator 31 in a rotatable manner.
  • the motor rotor 32 is connected to the axial end portion of the screw shaft 4, and is located on the same axial line as the screw rotor 5.
  • the electric motor 30 drives and rotates the screw shaft 4 to rotate the screw rotor 5.
  • the electric motor 30 is driven by an inverter at a variable rotational speed although illustrations of the inverter are omitted.
  • the electric motor 30 is operated while increasing or decreasing the rotational speed of the screw shaft 4.
  • FIG. 3 is an explanatory view illustrating a suctioning process that is operation of a compression portion of the screw compressor according to the embodiment of the present invention.
  • Fig. 4 is an explanatory view illustrating a compressing process that is operation of the compression portion of the screw compressor according to the embodiment of the present invention.
  • Fig. 5 is an explanatory view illustrating a discharging process that is operation of the compression portion of the screw compressor according to the embodiment of the present invention. Note that the respective processes are described with a focus on the compression chamber 20 illustrated by dotted hatching in Figs. 3 to 5 .
  • the screw rotor 5 is rotated through the screw shaft 4 by the electric motor 30, so that the gate-rotor tooth portions 6a of the gate rotors 6 move within, and relative to, the tooth grooves 5a forming the compression chamber 20.
  • the suctioning process ( Fig. 3 ), the compressing process ( Fig. 4 ), and the discharging process ( Fig. 5 ) are considered as one cycle, and this cycle is repeated.
  • Fig. 3 illustrates the state of the compression chamber 20 in the suctioning process.
  • the screw rotor 5 is driven by the electric motor 30 and is rotated in a direction shown by the solid arrow. Due to this rotation, the volume of the compression chamber 20 is decreased as illustrated in Fig. 4 .
  • the compression chamber 20 communicates with the discharge port 8a as illustrated in Fig. 5 .
  • This allows refrigerant gas at high pressure, compressed in the compression chamber 20, to be discharged from the discharge port 8a to the outside.
  • Refrigerant gas is compressed again on the back side of the screw rotor 5 in the same manner as described above.
  • the screw compressor 100 To minimize the decrease in operational efficiency in the screw compressor 100, it is effective to reduce the leakage of fluid being compressed by setting a small clearance between the outer circumferential surface of the screw rotor 5 and the inner cylindrical surface of the casing 1, and between the outer circumferential surface of the screw rotor 5 and the slide valve 8.
  • the screw rotor 5 and the slide valve 8 may thermally expand due to an increase in temperature of the refrigerant gas compressed in the compression chamber 20, and this may result in a reduction in the clearance between the outer circumferential surface of the screw rotor 5 and the inner cylindrical surface of the casing 1, and between the outer circumferential surface of the screw rotor 5 and the slide valve 8.
  • the screw rotor 5 may rotate reversely due to a difference between higher pressure and lower pressure in the casing 1.
  • the valve body portion 80 of the slide valve 8 may fall toward the screw rotor 5 or may rotate in the circumferential direction due to a change in internal pressure in the compression chamber 20 and other influences.
  • the valve body portion 80 of the slide valve 8 may fall toward the screw rotor 5 or may rotate in the circumferential direction due to a change in pressure to be applied from the compression chamber 20. That is, when the clearance between the slide valve 8 and the screw rotor 5 is excessively small, the slide valve 8 may contact the screw rotor 5, and this may cause burning or other problems.
  • Fig. 6 is an enlarged cross-sectional view illustrating principal parts of the screw compressor according to an example useful for understanding the present invention.
  • key grooves 13 and 14 with a rectangular shape are formed facing each other on the outer surface of the slide valve 8 and on the inner surface of the casing 1, respectively.
  • a key 15 common to the key grooves 13 and 14 is inserted in the key grooves 13 and 14.
  • the key 15 is formed into a rectangular shape to be fitted in the key grooves 13 and 14 with a rectangular shape. That is, rotation of the slide valve 8 in the circumferential direction is restricted by the key grooves 13 and 14 and the key 15.
  • the rectangular shape of the key grooves 13 and 14 means that the key grooves 13 and 14 have the rectangular shape when the slide valve 8 is viewed in vertical cross-section. Between the key 15 and the key grooves 13 and 14, a slight clearance is formed which is necessary for the slide valve 8 to be slidably moved in the rotational-axis direction.
  • the key groove 13 formed on the slide valve 8, and the key groove 14 formed on the casing 1 are configured to have an identical shape with an identical size. However, the key grooves 13 and 14 may be configured to have different shapes with different sizes.
  • the key groove 13 formed on the slide valve 8 may be formed in the guide portion 81 or may be formed in the valve body portion 80.
  • the key 15 is made of material with a smaller linear expansion coefficient than linear expansion coefficients of the materials of the slide valve 8 and the casing 1.
  • components in the vicinity of the screw rotor 5 may reach high temperature depending on the operational conditions, and thus the casing 1, the slide valve 8, and the key 15 may thermally expand. Even in this case, a slight clearance can be secured between the key 15 and the key grooves 13 and 14, so that the slide valve 8 can still be slidably moved in the rotational-axis direction of the screw rotor 5.
  • the screw compressor 100 includes the casing 1 forming an outer shell, the screw shaft 4 with one end thereof connected with the drive portion 3 to be rotationally driven, the screw rotor 5 including the tooth grooves 5a with a spiral shape on the outer circumferential surface of the screw rotor 5, the screw rotor 5 being fixed to the screw shaft 4, the gate rotor 6 including a plurality of the gate-rotor tooth portions 6a to be fitted in the tooth grooves 5a of the screw rotor 5, the gate rotor 6 forming the compression chamber 20 together with the casing 1 and the screw rotor 5, and the slide valve 8 provided in the slide groove 12 formed on the inner cylindrical surface of the casing 1 in a slidably movable manner in the rotational-axis direction of the screw rotor 5.
  • the key grooves 13 and 14 are formed facing each other on the outer surface of the slide valve 8 and on the inner surface of the casing 1, respectively.
  • the key 15 common to the key grooves 13 and 14 is inserted in the key grooves 13 and
  • the screw compressor 100 can prevent the slide valve 8 from contacting the screw rotor 5 since the slide valve 8 does not rotate in the circumferential direction even when there may be variations in the pressure applied to the inner cylindrical surface of the slide valve 8, the inner cylindrical surface facing the outer circumferential surface of the screw rotor 5. Consequently, the screw compressor 100 can be achieved as a reliable screw compressor that can secure a clearance between the slide valve 8 and the screw rotor 5, while minimizing a decrease in efficiency in the compressor by reducing the clearance between the slide valve 8 and the screw rotor 5 as small as possible.
  • FIG. 7 is an enlarged cross-sectional view illustrating principal parts of the screw compressor according to Embodiment 1 of the present invention. Note that the constituent components that are the same as those of the screw compressor 100 described above are denoted by the same reference signs, and descriptions thereof are appropriately omitted.
  • key grooves 16 and 17 with a dovetail groove-like shape are formed facing each other on the outer surface of the slide valve 8 and on the inner surface of the casing 1, respectively.
  • a key 18 common to the key grooves 16 and 17 is inserted in the key grooves 16 and 17.
  • the key 18 is formed with its upper and lower portions relative to the midsection being formed into a dovetail shape corresponding to the dovetail groove-like shape of the key grooves 16 and 17. That is, rotation of the slide valve 8 in the circumferential direction, and movement of the slide valve 8 in the radial direction are restricted by the key grooves 16 and 17 and the key 18.
  • the dovetail groove-like shape of the key grooves 16 and 17 means that the key grooves 16 and 17 have a trapezoidal shape when the slide valve 8 is viewed in vertical cross-section. Between the key 18 and the key grooves 16 and 17, a slight clearance is formed which is necessary for the slide valve 8 to be slidably moved in the rotational-axis direction.
  • the key groove 16 formed on the slide valve 8, and the key groove 17 formed on the casing 1 are configured to have an identical shape with an identical size. However, the key grooves 16 and 17 may be configured to have different shapes with different sizes.
  • the key groove 16 formed on the slide valve 8 may be formed in the guide portion 81 or may be formed in the valve body portion 80.
  • the key 18 is made of material with a smaller linear expansion coefficient than linear expansion coefficients of the materials of the slide valve 8 and the casing 1.
  • the screw compressor 101 can prevent the slide valve 8 from contacting the screw rotor 5 since the slide valve 8 does not rotate in the circumferential direction or move in the radial direction even when there may be variations in the pressure applied to the inner cylindrical surface of the slide valve 8, the inner cylindrical surface facing the outer circumferential surface of the screw rotor 5. Consequently, the screw compressor 100 can be achieved as a reliable screw compressor that can secure a clearance between the slide valve 8 and the screw rotor 5, while minimizing a decrease in efficiency in the compressor by reducing the clearance between the slide valve 8 and the screw rotor 5 as small as possible.
  • FIG. 8 is an enlarged cross-sectional view illustrating principal parts of the screw compressor according to the example. Note that the constituent components that are the same as those of the screw compressor 100 described above are denoted by the same reference signs, and descriptions thereof are appropriately omitted.
  • the key groove 14 with a rectangular shape is formed on the inner surface of the casing 1, which is one of the outer surface of the slide valve 8 and the inner surface of the casing 1, and a projecting portion 15a having a rectangular shape to be fitted in the key groove 14 is formed on the outer surface of the slide valve 8. That is, the screw compressor 102 according to the example is characterized in that the key 15 described above is provided integrally with the slide valve 8. Thus, the screw compressor 102 according to the example can omit the key 15 and accordingly reduce the number of parts, and consequently can contribute to a cost reduction and improve product management.
  • the screw compressor 102 can prevent the slide valve 8 from contacting the screw rotor 5 since the slide valve 8 does not rotate in the circumferential direction even when there may be variations in the pressure applied to the inner cylindrical surface of the slide valve 8, the inner cylindrical surface facing the outer circumferential surface of the screw rotor 5. Consequently, the screw compressor 102 can be achieved as a reliable screw compressor that can secure a clearance between the slide valve 8 and the screw rotor 5, while minimizing a decrease in efficiency in the compressor by reducing the clearance between the slide valve 8 and the screw rotor 5 as small as possible.
  • Fig. 9 is an enlarged cross-sectional view illustrating principal parts of a modification of the screw compressor shown in Fig. 8 .
  • the key groove 13 with a rectangular shape is formed on the outer surface of the slide valve 8, which is one of the outer surface of the slide valve 8 and the inner surface of the casing 1, and a projecting portion 15b having a rectangular shape to be fitted in the key groove 13 is formed on the inner surface of the casing 1.
  • the screw compressor 102 illustrated in Fig. 9 also achieves the same effects as those obtained from the configuration illustrated in Fig. 8 .
  • FIG. 10 is an enlarged cross-sectional view illustrating principal parts of the screw compressor according to Embodiment 2 of the present invention. Note that the constituent components that are the same as those of the screw compressors 100 and 101 described above are denoted by the same reference signs, and descriptions thereof are appropriately omitted.
  • the key groove 17 with a dovetail groove-like shape is formed on the inner surface of the casing 1, which is one of the outer surface of the slide valve 8 and the inner surface of the casing 1, and a projecting portion 18a having a dovetail shape to be fitted in the key groove 17 is formed on the outer surface of the slide valve 8.
  • the screw compressor 103 according to Embodiment 2 is characterized in that the key 18 described above is provided integrally with the slide valve 8.
  • the screw compressor 103 according to Embodiment 2 can omit the key 18 and accordingly reduce the number of parts, and consequently can contribute to a cost reduction and improve product management.
  • the screw compressor 103 can be achieved as a reliable screw compressor that can secure a clearance between the slide valve 8 and the screw rotor 5, while minimizing a decrease in efficiency in the compressor by reducing the clearance between the slide valve 8 and the screw rotor 5 as small as possible.
  • Fig. 11 is an enlarged cross-sectional view illustrating principal parts of a modification of the screw compressor according to Embodiment 2 of the present invention.
  • the key groove 16 with a dovetail groove-like shape is formed on the outer surface of the slide valve 8, which is one of the outer surface of the slide valve 8 and the inner surface of the casing 1, and a projecting portion 18b having a dovetail shape to be fitted in the key groove 16 is formed on the inner surface of the casing 1.
  • the screw compressor 103 according to Embodiment 2 illustrated in Fig. 11 also achieves the same effects as those obtained from the configuration illustrated in Fig. 10 .
  • the present invention is not limited to the configuration according to the above embodiments.
  • the internal configuration of the screw compressor 100 is not limited to the particulars described above, but may include other constituent elements.
  • the screw compressor 100 has been described by using a single-stage single screw compressor as an example, but may be, for example, a two-stage single screw compressor.
  • the slide valve 8 is not limited to the internal volume-ratio regulating valve, but may be configured to regulate the compression capacity, for example.
  • the number of the gate rotors 6 is not limited to two as illustrated in the drawings, but may be one.
  • the shape of the key groove is not limited to the rectangular shape or the dovetail groove-like shape, but may be another shape.
  • the key or the projecting portion has a shape corresponding to the key groove.
  • the present invention includes a range of design changes and application variations usually made by those skilled in the art without departing from the technical scope of the present invention as defined by the appended claims.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (3)

  1. Compresseur à vis (100), comprenant :
    un carter (1) formant une enveloppe extérieure ;
    un arbre à vis (4) situé dans le carter (1), l'arbre à vis (4) étant configuré pour être entraîné en rotation ;
    un rotor à vis (5) fixé à l'arbre à vis (4), le rotor à vis (5) incluant une rainure de dent (5a) avec une forme de spirale sur une surface circonférentielle extérieure du rotor à vis (5) ;
    un rotor femelle (6) incluant une pluralité de parties de dent de rotor femelle (6a) destinées à être ajustées dans la rainure de dent (5a) du rotor à vis (5), le rotor femelle (6) formant une chambre de compression (20) conjointement avec le carter (1) et le rotor à vis (5) ; et
    une soupape coulissante (8) prévue dans une rainure de coulissement (12) formée sur une surface cylindrique intérieure du carter (1), la soupape coulissante (8) étant configurée pour être mobile de façon coulissante dans une direction d'axe de rotation du rotor à vis (5), caractérisé en ce que
    des rainures de clavette (16, 17) sont formées se faisant face l'une à l'autre sur une surface extérieure de la soupape coulissante (8) et sur une surface intérieure du carter (1), et une clavette (18) commune aux rainures de clavette (16, 17) est insérée dans les rainures de clavette (16, 17),
    dans lequel chacune des rainures de clavette (16, 17) a une forme de type rainure trapézoïdale et en queue d'aronde.
  2. Compresseur à vis (100), comprenant :
    un carter (1) formant une enveloppe extérieure ;
    un arbre à vis (4) situé dans le carter (1), l'arbre à vis (4) étant configuré pour être entraîné en rotation ;
    un rotor à vis (5) fixé à l'arbre à vis (4), le rotor à vis (5) incluant une rainure de dent (5a) avec une forme de spirale sur une surface circonférentielle extérieure du rotor à vis (5) ;
    un rotor femelle (6) incluant une pluralité de parties de dent de rotor femelle (6a) destinées à être ajustées dans la rainure de dent (5a) du rotor à vis (5), le rotor femelle (6) formant une chambre de compression (20) conjointement avec le carter (1) et le rotor à vis (5) ; et
    une soupape coulissante (8) prévue dans une rainure de coulissement (12) formée sur une surface cylindrique intérieure du carter (1), la soupape coulissante (8) étant configurée pour être mobile de façon coulissante dans une direction d'axe de rotation du rotor à vis (5), caractérisé en ce que
    une rainure de clavette (16, 17) est formée sur une d'une surface extérieure de la soupape coulissante (8) et d'une surface intérieure du carter (1), et une partie saillante (18a, 18b) destinée à être ajustée dans la rainure de clavette (16, 17) est formée sur une autre,
    dans lequel la rainure de clavette (16, 17) a une forme de type rainure trapézoïdale et en queue d'aronde.
  3. Compresseur à vis (100) selon la revendication 1, dans lequel la clavette (18) est faite de matériau avec un coefficient de dilatation linéaire plus petit que des coefficients de dilatation linéaire de matériaux de la soupape coulissante (8) et du carter (1).
EP18927914.4A 2018-07-27 2018-07-27 Compresseur à vis Active EP3832138B1 (fr)

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Application Number Priority Date Filing Date Title
PCT/JP2018/028273 WO2020021707A1 (fr) 2018-07-27 2018-07-27 Compresseur à vis

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EP3832138B1 true EP3832138B1 (fr) 2023-12-20

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* 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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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS55140781U (fr) * 1979-03-30 1980-10-07
JPS6332389Y2 (fr) * 1981-02-12 1988-08-29
JP2509798Y2 (ja) * 1990-04-16 1996-09-04 石川島播磨重工業株式会社 機械駆動式過給機
JP4311500B2 (ja) 2007-12-17 2009-08-12 ダイキン工業株式会社 スクリュー圧縮機
JP2013060877A (ja) 2011-09-13 2013-04-04 Daikin Industries Ltd スクリュー圧縮機
JP5790452B2 (ja) * 2011-12-01 2015-10-07 ダイキン工業株式会社 スクリュー圧縮機

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