WO2021100165A1 - 回転式圧縮機、冷凍サイクル装置および回転式圧縮機の製造方法 - Google Patents

回転式圧縮機、冷凍サイクル装置および回転式圧縮機の製造方法 Download PDF

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Publication number
WO2021100165A1
WO2021100165A1 PCT/JP2019/045596 JP2019045596W WO2021100165A1 WO 2021100165 A1 WO2021100165 A1 WO 2021100165A1 JP 2019045596 W JP2019045596 W JP 2019045596W WO 2021100165 A1 WO2021100165 A1 WO 2021100165A1
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WO
WIPO (PCT)
Prior art keywords
vane
cylinder
spring
spring guide
rotary compressor
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.)
Ceased
Application number
PCT/JP2019/045596
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English (en)
French (fr)
Japanese (ja)
Inventor
尚久 五前
宏樹 長澤
勝俊 辰己
亮 濱田
拓真 塚本
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2019/045596 priority Critical patent/WO2021100165A1/ja
Priority to CN201980101219.1A priority patent/CN114651129A/zh
Priority to CZ2022-194A priority patent/CZ2022194A3/cs
Priority to JP2021558112A priority patent/JP7146116B2/ja
Publication of WO2021100165A1 publication Critical patent/WO2021100165A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • 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

Definitions

  • the present invention relates to a method for manufacturing a rotary compressor, a refrigeration cycle device, and a rotary compressor used in a refrigeration cycle of an air conditioner, a refrigerator, a refrigerator, or the like.
  • the rotary compressor has an annular cylinder housed in a closed container, a rolling piston that rotates eccentrically in the cylinder, and vanes slidably arranged in a vane groove provided in the cylinder.
  • the vane is urged by a vane spring so that the tip of the vane is constantly in contact with the rolling piston, and the space inside the cylinder is divided into a low pressure space and a high pressure space. Then, the rolling piston moves eccentrically in the cylinder, so that the volume of the low-pressure space is reduced to become a high-pressure space, and the refrigerant sucked into the cylinder is compressed.
  • the vane spring that urges the vane is housed in the vane spring insertion hole formed in the cylinder and held in the cylinder.
  • the length of the vane spring cannot be made longer because the distance between the end surface on the rear end side of the vane and the inner peripheral surface of the closed container is restricted. .. Therefore, when the vane moves to the rearmost top dead center position of the reciprocating motion, the total length of the vane spring reaches the close contact length at which the vane spring is maximally contracted, and the stress generated in the vane spring becomes large.
  • the spring may be damaged by fatigue.
  • the vane spring repeats the expansion and contraction operation while pressing the vane in the closed container. Therefore, if there is a deviation in the mounting position and mounting posture of the vane spring, interference between the vane spring and peripheral parts and bending of the vane spring occur during the expansion and contraction operation of the vane spring. This causes problems such as damage to the vane spring, malfunction, and shortened life. Therefore, it is required to accurately assemble the vane spring to the rotary compressor.
  • the rotary compressor of Patent Document 1 has a configuration in which a vane spring is arranged in a spring guide that protrudes and is fixed to the outside of a closed container.
  • the internal pressure of the compressed refrigerant acts on the closed container, and the closed container changes its shape, such as expanding outward.
  • the structure is such that the spring guide is fixed to the closed container, the position of the vane spring may deviate from the regular position due to the deformation of the closed container due to the internal pressure, and the vane spring can be installed accurately. Can not.
  • the present invention has been made in view of the above circumstances, and provides a method for manufacturing a rotary compressor, a refrigeration cycle device, and a rotary compressor capable of accurately installing a vane spring on a cylinder.
  • the purpose is.
  • the rotary compressor according to the present invention includes a closed container, an annular cylinder housed in the closed container, a rolling piston that eccentrically rotates along the inner peripheral surface of the cylinder, and a vane groove provided in the cylinder in the radial direction. It is equipped with a vane that reciprocates inside, a vane spring that urges the vane to bring the tip of the vane into contact with the rolling piston, and a tubular spring guide that fixes the vane spring inside, and the spring guide is sealed. It is provided so as to penetrate the container, and one end of the spring guide is fixed to a fixing recess formed on the outer peripheral surface of the cylinder.
  • the vane spring since the spring guide in which the vane spring is fixed inside is directly fixed to the cylinder, the vane spring can be installed accurately on the cylinder.
  • FIG. 5 is an enlarged cross-sectional view showing a compression mechanism portion in the rotary compressor according to the first embodiment. It is an enlarged view which shows the joint structure of the spring guide and the cylinder of the rotary compressor which concerns on Embodiment 1.
  • FIG. It is a figure which shows the configuration example for increasing the fixing force of the fixing part of a cylinder and a spring guide in the rotary compressor which concerns on Embodiment 1.
  • FIG. It is a figure which shows the example which provided the groove in the axial direction in the spring guide in the rotary compressor which concerns on Embodiment 1.
  • FIG. 5 is an enlarged cross-sectional view of a spring guide of the rotary compressor according to the first embodiment.
  • FIG. 5 is an enlarged cross-sectional view of a modified example of a spring guide of the rotary compressor according to the first embodiment. It is a flowchart which shows the manufacturing method of the main part of the rotary compressor which concerns on Embodiment 1.
  • FIG. It is a figure which shows the refrigerant circuit of the refrigerating cycle apparatus which concerns on Embodiment 2.
  • a rotary compressor used for an air conditioner, a refrigerator, a refrigerator, or the like will be described as an example.
  • FIG. 1 is a cross-sectional view showing a schematic configuration of the rotary compressor according to the first embodiment.
  • FIG. 2 is an enlarged cross-sectional view showing a compression mechanism portion in the rotary compressor according to the first embodiment.
  • FIG. 3 is an enlarged view showing a joint structure of a spring guide and a cylinder of the rotary compressor according to the first embodiment.
  • the terms “diameter”, “circumferential”, and “axial” refer to the “diameter”, “circumferential”, and “axial” of the cylinder, respectively, without particular notice. And.
  • the rotary compressor 1 includes an electric element 25, a compression element 10 for compressing the refrigerant, and a rotating shaft 17 for transmitting the driving force of the electric element 25 to the compression mechanism portion inside the closed container 5. ..
  • the closed container 5 is a closed container having a substantially cylindrical shape.
  • the thickness of the closed container 5 is formed so that the closed container 5 is not distorted by the internal pressure of the refrigerant compressed by the compression element 10. Further, by increasing the wall thickness of the closed container 5, when the rotary compressor 1 is attached to a device such as an air conditioner or a refrigerator by, for example, arc spot welding, the influence of distortion of the closed container 5 caused by heating can be reduced. It can be made difficult to apply to the compression element 10.
  • An accumulator 28 for muting the refrigerant noise is provided on the outside of the closed container 5 adjacent to the closed container 5.
  • the accumulator 28 is connected to each of the two compression mechanisms described later that constitute the compression element 10 via an accumulator tube 29.
  • a discharge pipe 16 for discharging the refrigerant compressed by the compression element 10 is connected to the upper part of the closed container 5.
  • Refrigerating machine oil for lubricating the compression element 10 is stored in the bottom of the closed container 5.
  • synthetic oils such as POE (polyol ester), PVE (polyvinyl ether) and AB (alkylbenzene) are used.
  • the electric element 25 includes a cylindrical stator 26 fixed to the inner peripheral surface of the closed container 5 and a cylindrical rotor 27 rotatably arranged inside the stator 26.
  • the stator 26 has an outer diameter larger than the inner diameter of the closed container 5, and is fixed to the inner peripheral surface of the closed container 5 by shrink fitting.
  • a magnetic pole is formed on the rotor 27 by a permanent magnet. The rotor 27 rotates by the action of the magnetic flux created by the magnetic poles on the rotor 27 and the magnetic flux created by the stator 26.
  • the electric element 25 and the compression element 10 are connected by a rotating shaft 17, the rotation of the electric element 25 is transmitted to the compression element 10, and the compressed element 10 compresses the refrigerant by the transmitted rotational force.
  • the refrigerant compressed by the compression element 10 is discharged into the closed container 5 through the discharge hole 21 (see FIG. 2) provided in the compression element 10. Therefore, the inside of the closed container 5 is filled with the compressed high-temperature and high-pressure refrigerant gas.
  • the compression element 10 includes two compression mechanisms arranged in the axial direction of the rotating shaft 17, an upper bearing 18, a lower bearing 19, and an intermediate plate 12. That is, the compression element 10 is a multi-cylinder type having two compression mechanisms.
  • the rotary compressor 1 is not limited to the multi-cylinder type having two or more compression mechanisms, and may be a one-cylinder type having one compression mechanism.
  • the compression mechanism includes a cylinder 11, a rolling piston 13, a vane 14, a vane spring 15, and a tubular spring guide 30 in which the vane spring 15 is fixed internally. ..
  • the cylinder 11 is composed of an annular flat plate.
  • the cylinder chamber 11a inside the cylinder 11 has both ends open in the axial direction, and is closed by one of the upper bearing 18 and the lower bearing 19 and the intermediate plate 12. Further, as shown in FIGS. 2 and 4, the cylinder 11 is formed with a suction port 20 penetrating in the radial direction and a discharge hole 21 formed on the inner peripheral surface 11b of the cylinder 11.
  • the accumulator tube 29 of the accumulator 28 is connected to the suction port 20.
  • the rolling piston 13 is housed in the cylinder chamber 11a of the cylinder 11 in a state of being rotatably fitted to the eccentric portion 17a of the rotating shaft 17.
  • the rolling piston 13 rotates eccentrically along the inner peripheral surface 11b of the cylinder 11.
  • the cylinder 11 is formed with a vane groove 22 that communicates with the cylinder chamber 11a and extends in the radial direction.
  • a vane 14 is arranged in the vane groove 22 so as to be able to advance and retreat in the radial direction.
  • a vane spring 15 is arranged on the back surface 14b side of the vane 14.
  • a housing recess for accommodating one end of the vane spring 15 is formed on the back surface 14b of the vane 14.
  • FIG. 2 shows a cross section of the accommodating recess, and one end of the vane spring 15 is fixed to the bottom surface of the accommodating recess. The other end of the vane spring 15 is fixed to the inner surface of the spring guide 30 described later.
  • the vane spring 15 urges the vane 14 to bring the tip portion 14a of the vane 14 into contact with the rolling piston 13.
  • the vane 14 is pressed inward in the radial direction by the urging force of the vane spring 15, so that the tip portion 14a of the vane 14 is always in contact with the rolling piston 13. In this way, the tip portion 14a of the vane 14 comes into contact with the rolling piston 13, so that the inside of the cylinder chamber 11a is partitioned into a low pressure space and a high pressure space.
  • the vane 14 reciprocates in the vane groove 22 with the tip portion 14a in contact with the outer peripheral surface 13c of the rolling piston 13 as the rolling piston 13 in the cylinder chamber 11a rotates eccentrically.
  • the vane spring 15 is a coil spring formed by winding a wire rod such as metal into a coil shape.
  • the vane spring 15 has a telescopic portion 15a that expands and contracts according to the movement of the vane 14, and a non-expandable portion 15b that is provided at an end portion of the elastic portion 15a in the elastic direction and does not expand and contract.
  • the wire rod is wound with a larger diameter than the stretchable portion 15a, and the wire rods are in close contact with each other and do not expand or contract.
  • the vane spring 15 is fixed in the tubular spring guide 30 by the non-expandable portion 15b.
  • the outer diameter of the non-stretchable portion 15b is formed to be larger than the inner diameter of the spring guide 30, and by press-fitting the non-stretchable portion 15b into the spring guide 30, the diameter of the non-stretchable portion 15b is reduced and the diameter is restored.
  • the vane spring 15 is fixed in the spring guide 30 by the restoring force.
  • the fixing of the vane spring 15 to the spring guide 30 is not limited to this fixing method, and the following method may be used.
  • a circumferential groove may be provided on the inner peripheral surface of the spring guide 30, and the non-expandable portion 15b may be fitted into the circumferential groove to fix the vane spring 15 to the spring guide 30.
  • a spiral groove matching the wire diameter of the vane spring 15 is provided on the inner peripheral surface of the spring guide 30, and the non-expandable portion 15b of the vane spring 15 is fitted into the spiral groove to guide the vane spring 15 to the spring guide. It may be fixed at 30.
  • the number of turns of the non-expandable portion 15b of the vane spring 15 is one, the following may be performed.
  • a groove for one turn matching the wire diameter of the vane spring 15 is provided on the inner peripheral surface of the spring guide 30, and the non-expandable portion 15b of the vane spring 15 is fitted into the groove for one turn to guide the vane spring 15. Fix at 30.
  • the spring guide 30 is provided so as to penetrate the closed container 5.
  • One end 30a of the spring guide 30 is inserted and fixed in a fixing recess 40 provided on the outer peripheral surface 11c of the cylinder 11, and the other end 30b passes through an opening 8 provided in the closed container 5 to be a closed container. It protrudes to the outside of 5.
  • the inner diameter of the opening 8 of the closed container 5 is larger than the outer diameter of the spring guide 30, and the spring guide 30 is fixed to the cylinder 11 without contacting the closed container 5.
  • the material of the spring guide 30 is preferably a high-strength material such as an iron material.
  • the spring guide 30 is not limited to a high-strength material such as an iron material, and may be made of a low-strength material such as resin.
  • a vane passing portion 31 is formed on the one end portion 30a side of the spring guide 30.
  • the vane passing portion 31 is composed of a slit extending in the axial direction of the spring guide 30 from the end surface of the spring guide 30 on the one end portion 30a side.
  • Two vane passing portions 31 are formed symmetrically with respect to the central axis of the spring guide 30.
  • the vane passing portion 31 is located on the radial extension line of the vane groove 22 in a state where the spring guide 30 is fixed to the cylinder 11 as shown in FIG.
  • the diameter D1 of the spring guide 30 is smaller than the axial length of the vane 14 (the length in the direction orthogonal to the paper surface of FIG. 3).
  • the radial width W1 of the vane passing portion 31 is larger than the width of the vane 14 in the same direction.
  • the spring guide 30 to which the vane spring 15 is fixed is arranged in a protruding portion 6 provided so as to project outward from the closed container 5.
  • the protruding portion 6 is a tubular member having a circular, rectangular or oval cross-sectional shape. As shown in FIG. 2, the projecting portion 6 is attached to the opening 8 formed in the closed container 5 so that the central axis of the projecting portion 6 is orthogonal to the central axis of the cylinder 11.
  • the protruding portion 6 is fixed to the closed container 5 by press-fitting the end portion of the protruding portion 6 into the opening 8 formed in the closed container 5.
  • a lid portion 7 is attached to an end portion of the protruding portion 6 opposite to the side fixed to the closed container 5 (hereinafter referred to as an outer peripheral side end portion).
  • the lid portion 7 is a lid that closes the outer peripheral side end portion of the protruding portion 6.
  • the lid portion 7 is joined to the outer peripheral side end portion of the protruding portion 6 by, for example, welding or brazing. By closing the outer peripheral end of the protrusion 6 with the lid 7, the protrusion 6 is sealed and the closed container 5 is sealed.
  • the rotating shaft 17 is rotated by the electric element 25.
  • the eccentric portion 17a moves eccentrically in the cylinder chamber 11a.
  • the rolling piston 13 eccentrically rotates in the cylinder chamber 11a, and the low-pressure gaseous refrigerant sucked into the cylinder chamber 11a from the accumulator tube 29 of the accumulator 28 is compressed.
  • the gaseous refrigerant compressed in the cylinder chamber 11a is discharged from the discharge hole 21 into the internal space of the closed container 5 when a predetermined pressure is reached.
  • the high-pressure gaseous refrigerant discharged into the internal space of the closed container 5 is discharged to the outside of the closed container 5 from the discharge pipe 16 provided in the closed container 5.
  • the vane 14 reciprocates in the vane groove 22 as the rolling piston 13 rotates.
  • the contact position between the outer peripheral surface 13c of the rolling piston 13 and the inner peripheral surface 11b of the cylinder 11 matches the phase of the arrangement position of the vane 14 (hereinafter, the rolling piston 13 is in the vane groove phase).
  • the vane 14 moves rearward in the direction away from the cylinder 11 and is located at the top dead center position.
  • the contact position between the outer peripheral surface 13c of the rolling piston 13 and the inner peripheral surface 11b of the cylinder 11 is 180 ° different from the phase of the arrangement position of the vane 14, the vane 14 is in the direction toward the center of the cylinder 11. It moves forward and is located at the bottom dead center position.
  • the vane 14 reciprocates between the top dead center position and the bottom dead center position. Further, when the rolling piston 13 is positioned in a phase rotated by 90 ° from the position shown in FIG. 2, the vane 14 is located at an intermediate position between the top dead center position and the bottom dead center position.
  • the range of reciprocating motion of the vane 14 is between the top dead center position and the bottom dead center position, and the spring of the vane 14 when the vane 14 is in the top dead center position, the bottom dead center position and the intermediate position.
  • the position of the guide 30 with respect to the vane passing portion 31 is as follows.
  • the back surface 14b of the vane 14 is located in the vane passing portion 31 of the spring guide 30. Further, when the vane 14 is in the bottom dead center position, the back surface 14b of the vane 14 is not located in the vane passing portion 31 of the spring guide 30. Further, even when the vane 14 is in the intermediate position, the back surface 14b of the vane 14 is not located in the vane passing portion 31 of the spring guide 30. The reason for this configuration is due to the convenience of manufacturing, but this point will be described later.
  • a so-called liquid back may occur in which the liquid refrigerant flows into the closed container 5.
  • the internal pressure of the cylinder chamber 11a rapidly increases, so that the vane 14 is pressed outward in the radial direction.
  • the vane 14 moves radially outward from the top dead center position, and stops when the back surface 14b of the vane 14 comes into contact with the bottom surface 31a of the vane passing portion 31 of the spring guide 30. That is, the bottom surface 31a of the vane passing portion 31 functions as a stopper for the vane 14 at the time of liquid backing.
  • the radial position of the bottom surface 31a of the vane passing portion 31 is set so that the length of the vane spring 15 does not become the close contact length when the back surface 14b of the vane 14 is in contact with the bottom surface 31a of the vane passing portion 31. There is. Therefore, when the internal pressure of the cylinder chamber 11a suddenly increases, such as during liquid backing, excessive pressure does not act on the vane spring 15.
  • the close contact length of the vane spring 15 is the length in which the vane spring 15 is contracted to the maximum and the wires are in close contact with each other.
  • the rotary compressor 1 of the first embodiment has a structure in which a protruding portion 6 is attached so as to project outward from the closed container 5. Therefore, in a sense, the outer shell of the rotary compressor 1 is expanded in the radial direction with respect to the installation portion of the vane spring 15. Therefore, the total length of the vane spring 15 can be freely set without being restricted by the distance between the back surface 14b of the vane 14 and the inner peripheral surface of the closed container 5.
  • the length of the vane spring 15 can be freely set by adjusting the length of the protruding portion 6. Therefore, the total length of the vane spring 15 can be extended and the expansion / contraction rate of the vane spring 15 can be reduced.
  • the expansion / contraction ratio of the vane spring 15 can be reduced, the fatigue resistance against stress repeatedly acting on the vane spring 15 can be sufficiently secured as compared with the case where a spring having a large expansion / contraction ratio is used. As a result, it is possible to increase the urging force that presses the vane 14 against the rolling piston 13 while ensuring the fatigue resistance.
  • the vane 14 moves to the rolling piston 13 when the vane 14 is in the bottom dead center position. I can't follow. That is, the tip portion 14a of the vane 14 is separated from the rolling piston 13. In this case, noise and vibration are generated.
  • the total length of the vane spring 15 can be freely set as described above, sufficient fatigue is obtained by extending the total length of the vane spring 15 and reducing the expansion / contraction ratio of the vane spring 15.
  • the bearing capacity can be secured. Therefore, it is possible to obtain the urging force required to constantly press the vane 14 against the rolling piston 13 while ensuring sufficient proof stress, and suppress noise and vibration generated when the vane 14 separates from the rolling piston 13. be able to.
  • the distance between the lid portion 7 and the spring guide 30 can be freely set by adjusting the length of the protruding portion 6, and the following effects can be obtained.
  • the distance between the lid portion 7 and the spring guide 30 is short, the heat generated when the lid portion 7 is joined to the protruding portion 6 by welding or brazing is transferred to the vane spring 15 via the lid portion 7 and vanes. The characteristics of the spring 15 may deteriorate.
  • the distance between the lid portion 7 and the spring guide 30 can be freely set. Therefore, by ensuring a sufficient distance, the vane spring 15 is generated by the heat transferred to the vane spring 15 at the time of joining. It is possible to prevent deterioration of the characteristics of.
  • the vane spring is arranged in the tubular spring guide provided so as to project outward from the closed container.
  • the spring guide together with the airtight container, is a component that forms a part of the outer shell of the rotary compressor, and the internal pressure of the refrigerant discharged from the compression element acts on these outer shell components.
  • the shape of the outer component changes, such as bulging outward due to the influence of internal pressure. Therefore, if the structure is such that the spring guide is fixed to the outer shell component, the spring guide and thus the vane spring cannot be arranged at the target position due to the influence of the deformation of the outer shell component due to the internal pressure.
  • the target position is a position along a direction orthogonal to the central axis of the cylinder 11.
  • the vane spring 15 is fixed to the spring guide 30, which is a separate component from the outer component, and the spring guide 30 is directly fixed to the cylinder 11. Therefore, the vane spring 15 can be installed with high accuracy, and the vane spring 15 can be operated stably.
  • the outer peripheral surface 11c of the cylinder 11 is provided with a cylindrical fixing recess 40 into which one end 30a of the spring guide 30 is fitted.
  • the fixed recess 40 is formed so as to extend radially inward from the outer peripheral surface 11c of the cylinder 11, and communicates with the vane groove 22 at the bottom surface of the fixed recess 40.
  • the inner diameter of the fixed recess 40 is formed to be smaller than the outer diameter of the spring guide 30, and one end 30a of the spring guide 30 is inserted into the open end of the fixed recess 40 and press-fitted.
  • the outer diameter of the spring guide 30 is, for example, 85% or less of the inner diameter of the protruding portion 6. This is due to the following reasons.
  • the cylinder 11 is fixed in the closed container 5 so that the central axis of the cylinder 11 coincides with the central axis of the closed container 5.
  • the central axis of the cylinder 11 may be installed at an angle with respect to the central axis of the closed container 5. If the central axis of the cylinder 11 is tilted with respect to the central axis of the closed container 5, the fixing recess 40 is also tilted.
  • the spring guide 30 is inserted into the protruding portion 6 fixed to the closed container 5 from the open end of the protruding portion 6 and fixed to the cylinder 11. Therefore, if the fixing recess 40 is tilted, the spring guide 30 also needs to be tilted and passed through the protrusion 6 when the spring guide 30 is inserted through the protrusion 6 during manufacturing.
  • the outer diameter of the spring guide 30 is, for example, more than 85% of the inner diameter of the protruding portion 6, the gap between the spring guide 30 and the protruding portion 6 is too small, and the spring guide 30 can be inserted at an angle. It may not be possible. Therefore, the outer diameter of the spring guide 30 is set to, for example, 85% or less of the inner diameter of the protruding portion 6.
  • the depth L2 of the fixed recess 40 of the cylinder 11 should be short for the following reasons.
  • the depth L2 of the fixed recess 40 is lengthened, the length L3 of the vane groove 22 in the same direction, that is, the length L3 of the portion in contact with the vane 14 is shortened accordingly, and the vane 14 slides the vane groove 22 at high speed. Burn-in is likely to occur when moving. Therefore, the depth L2 of the fixing recess 40 should be short, and should be 10% or less of the outer diameter D2 of the cylinder 11.
  • the spring guide 30 is attached to the fixing portion between the fixing recess 40 of the cylinder 11 and the one end portion 30a of the spring guide 30.
  • a force is applied in the direction of pulling out from the cylinder 11. Therefore, a sufficient fixing force is required for the fixing portion of the fixing recess 40 of the cylinder 11 and the one end portion 30a of the spring guide 30. Therefore, in order to increase the fixing force of the fixing portion between the cylinder 11 and the spring guide 30, a part or all of the following methods (1) to (3) may be adopted.
  • the outer peripheral surface of one end 30a of the spring guide 30 is treated with a chemical or the like to make the surface roughness larger than the inner peripheral surface of the spring guide 30, and friction with the inner peripheral surface of the fixed recess 40 of the cylinder 11. May be increased to increase the fixing force.
  • FIG. 4 is a diagram showing a configuration example for increasing the fixing force of the fixing portion between the cylinder and the spring guide in the rotary compressor according to the first embodiment.
  • the metal adhesive 34 may be applied at an appropriate position to assist fixing.
  • FIG. 4 shows an example in which the metal adhesive 34 is applied to the connecting corner portion between the spring guide 30 and the cylinder 11, but the configuration is not limited to this.
  • the metal adhesive 34 may be applied to a part or all of the outer peripheral surface of one end 30a of the spring guide 30, the inner peripheral surface of the fixing recess 40 of the cylinder 11, and the connecting angle portion between the spring guide 30 and the cylinder 11. ..
  • FIGS. 5 and 6 show an example in which the spring guide 30 is provided with a groove.
  • FIG. 5 is a diagram showing an example in which a groove in the axial direction is provided in the spring guide in the rotary compressor according to the first embodiment.
  • FIG. 6 is a diagram showing an example in which a groove in the circumferential direction is provided in the spring guide in the rotary compressor according to the first embodiment.
  • FIG. 5A is a cross-sectional view of the spring guide 30, and
  • FIG. 6B is a plan view of the spring guide 30.
  • a groove or a machining mark is provided on the inner peripheral surface of the fixing recess 40 of the cylinder 11 in the circumferential direction, and one end of the spring guide 30 is provided.
  • a groove 30c or a machining mark is provided on the outer peripheral surface of the portion 30a in the axial direction.
  • the direction in which the groove or machining mark is provided is reversed, and the groove or machining mark is provided in the axial direction on the inner peripheral surface of the fixing recess 40 of the cylinder 11, and on the outer peripheral surface of one end 30a of the spring guide 30, FIG.
  • the groove 30c or the processing mark may be provided in the circumferential direction. Further, the groove or the machining mark may be provided on the inner peripheral surface of the fixing recess 40 of the cylinder 11 at an angle, and the groove or the machining mark may be provided on the outer peripheral surface of one end 30a of the spring guide 30 at an angle in the opposite direction. ..
  • the processing mark is a portion whose surface is roughly formed by processing.
  • the method of joining the spring guide 30 to the cylinder 11 is a press-fitting method, but the method is not limited to this, and the screw fixing method shown in FIG. 7 below may be used.
  • FIG. 7 is an enlarged view showing a modified example of the joint structure between the spring guide and the cylinder of the rotary compressor according to the first embodiment.
  • a female screw portion 41 is formed on the inner peripheral surface of the fixing recess 40 of the cylinder 11.
  • a male screw portion 32 is formed on the outer peripheral surface of one end portion 30a of the spring guide 30. The length of the male screw portion 32 in the central axis direction of the spring guide 30 is formed to be longer than the length of the portion screwed into the fixing recess 40.
  • the spring guide 30 is fixed to the cylinder 11 by screw-fastening the male screw portion 32 of the spring guide 30 and the female screw portion 41 of the cylinder 11.
  • the shape of the male screw portion 32 of the spring guide 30 may be an asymmetric screw shown in FIG. 8 below.
  • FIG. 8 is an enlarged cross-sectional view of the spring guide of the rotary compressor according to the first embodiment.
  • the male threaded portion 32 of the spring guide 30 is an asymmetric thread in which the center of the thread 33 is inclined to one side.
  • the angle ⁇ formed by one side of the screw thread 33 with a plane orthogonal to the central axis of the spring guide 30 and the angle ⁇ formed by the opposite side of the screw thread 33 with a plane orthogonal to the central axis of the spring guide 30 are different. ing.
  • ⁇ > ⁇ is set, but ⁇ ⁇ may be set.
  • the inclination direction of the screw thread 33 is the same in the entire male screw portion 32, but it may be as shown in FIG. 9 below.
  • FIG. 9 is an enlarged cross-sectional view of a modified example of the spring guide of the rotary compressor according to the first embodiment.
  • a part of the male screw portion 32 of the spring guide 30 is inclined toward the tip end side in the insertion direction (left side in FIG. 9), and a part is inclined toward the rear end side in the insertion direction.
  • the thread on the tip side in the insertion direction of the male screw portion 32 is tilted toward the tip side in the insertion direction
  • the thread on the rear end side in the insertion direction is tilted toward the rear end side in the insertion direction. This is just an example, and is not limited to the illustrated example.
  • the spring guide 30 is provided with a male threaded portion and the cylinder 11 is provided with a female threaded portion, the spring guide 30 may be provided with a female threaded portion and the cylinder 11 may be provided with a male threaded portion.
  • FIG. 10 is a flowchart showing a method of manufacturing a main part of the rotary compressor 1 according to the first embodiment.
  • the cylinder 11 is fixed in the closed container 5 to which the protruding portion 6 is joined, and the rolling piston 13 is inserted into the cylinder 11 (step S1).
  • the compression element 10 is configured to include a plurality of compression mechanisms, the rotating shaft 17 including the upper bearing 18, the two cylinders 11, the intermediate plate 12, the lower bearing 19, and the two rolling pistons 13.
  • the integrated product which is a combination of and is fixed to the inside of the closed container 5.
  • Each cylinder 11 is fixed to the closed container 5 at a position where the fixing recess 40 faces the opening 8 of the closed container 5.
  • step S2 a step of inserting the vane 14 from the open end of the protrusion 6 into the vane groove 22 of one of the two cylinders 11 fixed to the closed container 5 is performed (step S2).
  • step S3 one end 30a of the spring guide 30 is inserted from the outside of the closed container 5 through the opening 8 of the closed container 5 and fixed to the fixing recess 40 of the cylinder 11 (step S3).
  • the spring guide 30 is inserted from the open end of the protrusion 6, and one end 30a is fixed to the fixing recess 40 of the cylinder 11 as described above.
  • the vane spring 15 is inserted into the spring guide 30 and fixed (step S4).
  • the vane 14, the spring guide 30, and the vane spring 15 are fixed to the other cylinder 11 in the same manner.
  • the lid portion 7 is joined to the protruding portion 6 (step S5).
  • the vane spring 15 is fixed to the spring guide 30 after the spring guide 30 is attached to the cylinder 11, but the reverse is also possible. That is, after fixing the vane spring 15 to the spring guide 30, the spring guide 30 to which the vane spring 15 is fixed may be attached to the cylinder 11.
  • one end of the vane spring 15 is fixed to the back surface 14b of the vane 14, and the other end is brought into contact with the lid 7 to hold the vane spring 15 in the protruding portion 6.
  • the vane spring 15 is fixed to the spring guide 30 joined to the cylinder 11 at the time when the lid portion 7 is joined to the protruding portion 6, so that the vane spring 15 is pressed. There is no need to hold it. Therefore, the assembleability is good.
  • the rotating shaft 17 is rotated to move the rolling piston 13 to the vane groove phase, and the vane 14 is moved to the bottom dead center position.
  • the vane spring 15 can be installed in a state where the length of the vane spring 15 is longer than when the vane 14 is located at the top dead center position, that is, the spring force acting on the vane spring 15 is small, and the vane spring 15 can be assembled. Is good.
  • the rolling piston 13 in one cylinder 11 and the rolling piston 13 in the other cylinder 11 are provided with a phase shift of 180 °. Therefore, when the rolling piston 13 in one cylinder 11 is located in the vane groove phase, the rolling piston 13 in the other cylinder 11 is located in a phase shifted by 180 ° from the vane groove phase. Therefore, when inserting the vane spring 15 into one of the cylinders 11, first, the rolling piston 13 is moved to a phase shifted by 180 ° from the vane groove phase, and the vane 14 is positioned at the bottom dead center position. Insert 15.
  • the spring guide 30 When the spring guide 30 is fixed to the cylinder 11 by a screw fixing method, one end portion 30a of the spring guide 30 is rotated in a state of being inserted into the fixing recess 40. Therefore, when rotating the spring guide 30, if the back surface 14b of the vane 14 is inside the vane passing portion 31 of the spring guide 30, the spring guide 30 cannot be rotated. Therefore, the spring guide 30 is rotated while the vane 14 is moved so that the back surface 14b of the vane 14 does not enter the vane passing portion 31. Specifically, for example, the vane 14 is moved to the bottom dead center position or the above-mentioned intermediate position.
  • the manufacturing process can be simplified. That is, in the above-mentioned assembly procedure, after fixing the spring guide 30 to one of the two cylinders 11, when fixing the spring guide 30 to the other cylinder 11, the rotating shaft 17 is rotated by 180 °. , It was necessary to move the position of the rolling piston 13. However, if the back surface 14b of the vane 14 is not located in the vane passing portion 31 when the rolling piston 13 is at a position rotated by 90 ° from the vane groove phase, the rotation of the rotating shaft 17 is unnecessary. That is, the spring guide 30 can be fixed to one cylinder 11 and then the spring guide 30 can be fixed to the other cylinder 11 while the rolling piston 13 is positioned at a position rotated by 90 ° from the vane groove phase.
  • the rotary compressor 1 of the first embodiment includes a closed container 5, an annular cylinder 11 housed in the closed container 5, a rolling piston 13 that eccentrically rotates along the inner peripheral surface 11b of the cylinder 11, and a cylinder.
  • the vane 14 reciprocates in the vane groove 22 provided in the radial direction of 11, the vane spring 15 that urges the vane 14 to bring the tip portion 14a of the vane 14 into contact with the rolling piston 13, and the vane spring 15. It is provided with a cylindrical spring guide 30 fixed inside.
  • the spring guide 30 is provided so as to penetrate the closed container 5, and one end portion 30a of the spring guide 30 is fixed to a fixing recess 40 formed on the outer peripheral surface of the cylinder 11.
  • the vane spring 15 can be installed with high accuracy on the cylinder 11. Therefore, the vane spring 15 can be operated stably.
  • the inner diameter of the opening 8 of the closed container 5 is larger than the outer diameter of the spring guide 30, and the spring guide 30 is fixed to the cylinder 11 without contacting the closed container 5.
  • the spring guide 30 can be fixed to the cylinder without being affected by the deformation of the closed container 5, so that the vane spring 15 can be installed accurately with respect to the cylinder 11.
  • the diameter of the fixing recess 40 is smaller than the outer diameter of one end 30a of the spring guide 30, and the spring guide 30 is press-fitted and fixed to the cylinder 11.
  • the spring guide 30 can be fixed to the cylinder 11 by press fitting.
  • the outer peripheral surface of one end 30a of the spring guide 30 has a greater roughness than the inner peripheral surface of the spring guide 30.
  • a metal adhesive is provided on a part or all of the outer peripheral surface of one end 30a of the spring guide 30, the inner peripheral surface of the fixing recess 40 of the cylinder 11, and the connecting angle portion between the spring guide 30 and the cylinder 11.
  • grooves or machining marks in different directions are formed on the outer peripheral surface of one end 30a of the spring guide 30 and the inner peripheral surface of the fixing recess 40 of the cylinder 11.
  • a male screw portion 32 is formed on one of the outer peripheral surface of one end 30a of the spring guide 30 and the inner peripheral surface of the fixing recess 40 of the cylinder 11, and a female screw portion 41 is formed on the other.
  • the spring guide 30 is fixed to the cylinder 11 by the means.
  • the spring guide 30 can be fixed to the cylinder 11 by screwing.
  • the male thread portion 32 is an asymmetric thread in which the center of the thread 33 is inclined to one side.
  • the thread 33 of the male thread portion 32 is partially inclined inward in the radial direction and partly inclined outward in the radial direction.
  • the spring guide 30 is provided with a vane passing portion 31 through which the vane 14 passes at a position where the vane groove 22 is extended in the radial direction.
  • the vane passing portion 31 of the spring guide 30 is a slit formed in the axial direction of the spring guide 30 from the end surface of the spring guide 30 on the one end portion 30a side.
  • the annular cylinder 11 is fixed in the closed container 5, and the rolling piston 13 is eccentrically rotated in the cylinder 11 along the inner peripheral surface 11b of the cylinder 11.
  • a step of inserting the vane 14 into the vane groove 22 formed in the cylinder 11 is provided.
  • the method of manufacturing the rotary compressor 1 further describes, one end portion 30a of the spring guide 30 in which the vane spring 15 for urging the vane 14 to bring the tip portion 14a of the vane 14 into contact with the rolling piston 13 is fixed inside.
  • the vane spring 15 can be installed with high accuracy on the cylinder 11. Therefore, it is possible to obtain the rotary compressor 1 capable of stably operating the vane spring 15.
  • the rotary compressor 1 includes a plurality of compression mechanisms.
  • the contact position between the outer peripheral surface 13c of the rolling piston 13 and the inner peripheral surface 11b of the cylinder 11 is 180 from the phase of the arrangement position of the vane 14. °
  • the position of the rolling piston 13 is moved so that the positions are in different phases.
  • the vane spring 15 can be installed in a state where the spring force acting on the vane spring 15 is small, and the assembling property is good.
  • the rotary compressor 1 includes a plurality of compression mechanisms.
  • the contact position between the outer peripheral surface 13c of the rolling piston 13 and the inner peripheral surface 11b of the cylinder 11 is 90 from the phase of the arrangement position of the vane 14. °
  • the position of the rolling piston 13 is moved so that the positions are in different phases.
  • the vane spring 15 can be installed in a state where the spring force acting on the vane spring 15 is small without moving the rolling piston 13 each time the vane spring 15 is installed in each of the cylinders 11, and the assembling property is good. .. That is, once, the position of the rolling piston 13 is moved so that the contact position between the outer peripheral surface 13c of the rolling piston 13 and the inner peripheral surface 11b of the cylinder 11 is in a phase different from the phase of the arrangement position of the vane 14 by 90 °. After that, the vane spring 15 can be installed in a state where the spring force acting on the vane spring 15 is small without moving the position of the rolling piston 13. As a result, the manufacturing process can be simplified.
  • the second embodiment relates to a refrigeration cycle apparatus including the rotary compressor 1 of the first embodiment.
  • FIG. 11 is a diagram showing a refrigerant circuit of the refrigeration cycle device according to the second embodiment.
  • the refrigeration cycle device 50 includes the rotary compressor 1 of the first embodiment, a condenser 51, an expansion valve 52 as a decompression device, and an evaporator 53.
  • the gas refrigerant discharged from the rotary compressor 1 flows into the condenser 51, exchanges heat with the air passing through the condenser 51, and flows out as a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant flowing out of the condenser 51 is depressurized by the expansion valve 52 to become a low-pressure gas-liquid two-phase refrigerant, which flows into the evaporator 53.
  • the low-pressure gas-liquid two-phase refrigerant flowing into the evaporator 53 exchanges heat with the air passing through the evaporator 53 to become a low-pressure gas refrigerant, which is again sucked into the rotary compressor 1.
  • the refrigeration cycle device 50 configured in this way is provided with the rotary compressor 1 of the first embodiment, so that stable operation of the vane 14 and the vane spring 15 can be obtained. Further, it is possible to prevent the spring guide 30 from coming off the cylinder 11. This makes it possible to configure a highly reliable refrigeration cycle device 50.
  • the refrigerating cycle device 50 can be applied to an air conditioner, a refrigerator, a refrigerator, or the like.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2019/045596 2019-11-21 2019-11-21 回転式圧縮機、冷凍サイクル装置および回転式圧縮機の製造方法 Ceased WO2021100165A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
PCT/JP2019/045596 WO2021100165A1 (ja) 2019-11-21 2019-11-21 回転式圧縮機、冷凍サイクル装置および回転式圧縮機の製造方法
CN201980101219.1A CN114651129A (zh) 2019-11-21 2019-11-21 旋转式压缩机、制冷循环装置以及旋转式压缩机的制造方法
CZ2022-194A CZ2022194A3 (cs) 2019-11-21 2019-11-21 Rotační kompresor, zařízení chladicího cyklu a způsob výroby rotačního kompresoru
JP2021558112A JP7146116B2 (ja) 2019-11-21 2019-11-21 回転式圧縮機、冷凍サイクル装置および回転式圧縮機の製造方法

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PCT/JP2019/045596 WO2021100165A1 (ja) 2019-11-21 2019-11-21 回転式圧縮機、冷凍サイクル装置および回転式圧縮機の製造方法

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CZ2022194A3 (cs) 2022-06-01
JPWO2021100165A1 (cs) 2021-05-27

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