WO2021100167A1 - 回転式圧縮機および冷凍サイクル装置 - Google Patents

回転式圧縮機および冷凍サイクル装置 Download PDF

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Publication number
WO2021100167A1
WO2021100167A1 PCT/JP2019/045599 JP2019045599W WO2021100167A1 WO 2021100167 A1 WO2021100167 A1 WO 2021100167A1 JP 2019045599 W JP2019045599 W JP 2019045599W WO 2021100167 A1 WO2021100167 A1 WO 2021100167A1
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WO
WIPO (PCT)
Prior art keywords
vane
spring
spring guide
cylinder
fixed
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/JP2019/045599
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
祐一朗 今川
宏樹 長澤
勝俊 辰己
尚久 五前
亮 濱田
拓真 塚本
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
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 JP2021558114A priority Critical patent/JP7275311B2/ja
Priority to PCT/JP2019/045599 priority patent/WO2021100167A1/ja
Priority to CN201980102291.6A priority patent/CN114729640B/zh
Priority to CZ2022-182A priority patent/CZ2022182A3/cs
Publication of WO2021100167A1 publication Critical patent/WO2021100167A1/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 rotary compressor and a refrigerating cycle device used in 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 an object of the present invention is to provide a rotary compressor and a refrigeration cycle device capable of accurately installing vane springs on a cylinder.
  • 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.
  • 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 explanatory drawing of the fixed structure of a vane spring and a spring guide in the rotary compressor which concerns on Embodiment 1.
  • FIG. It is a figure which shows the modification 1 of the spring guide of the rotary compressor which concerns on Embodiment 1.
  • FIG. It is explanatory drawing of the fixed structure of a vane spring and a spring guide in the rotary compressor which concerns on Embodiment 2.
  • FIG. It is explanatory drawing of the fixed structure of a vane spring and a spring guide in the rotary compressor which concerns on Embodiment 3.
  • FIG. It is explanatory drawing of the modification of the fixed structure of a vane spring and a spring guide in the rotary compressor which concerns on Embodiment 3.
  • FIG. It is explanatory drawing of the fixed structure of a vane spring and a spring guide in the rotary compressor which concerns on Embodiment 4.
  • FIG. It is a figure which shows the refrigerant circuit of the refrigerating cycle apparatus in Embodiment 5.
  • 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 a plurality of 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 cylindrical 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 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 spring guide 30 is made of 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.
  • One end of the spring guide 30 is fixed to a fixing recess 40 provided in the cylinder 11, and the other end of the spring guide 30 projects to the outside of the closed container 5 through an opening 8 provided in the closed container 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 spring guide 30 is fixed to the cylinder 11 by fitting, press-fitting, screw fixing, or the like.
  • the screw fixing is a method in which a male screw portion is provided on one of the outer peripheral surface of the spring guide 30 and the inner peripheral surface of the fixing recess 40 of the cylinder 11 and a female screw portion is provided on the other, and screwed and fastened.
  • a vane passing portion 31 is formed on one end 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 on the one end side of the spring guide 30.
  • 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 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 with respect to the guide 30 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 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 first embodiment relates to a structure in which the vane spring 15 is fixed to the spring guide 30 by a press-fitting method.
  • FIG. 4 is an explanatory view of a fixed structure of a vane spring and a spring guide in the rotary compressor according to the first embodiment.
  • the vane spring 15 is a coil spring formed by winding a wire rod such as metal in a coil shape.
  • the vane spring 15 has a small diameter portion 15a and a large diameter portion 15b having a diameter larger than that of the small diameter portion 15a.
  • the small diameter portion 15a has a non-expandable portion 15aa and a telescopic portion 15ab that expands and contracts following the movement of the vane 14.
  • the non-expandable portion 15aa and the large-diameter portion 15b of the small diameter portion 15a do not expand and contract because the wires are in close contact with each other.
  • the vane spring 15 is fixed in the tubular spring guide 30 with a large diameter portion 15b. That is, the large diameter portion 15b of the vane spring 15 is press-fitted into the spring guide 30, so that the diameter of the large diameter portion 15b is reduced, and the vane spring 15 is fixed in the spring guide 30 by the restoring force for returning the diameter. ing.
  • spring guide 30 shown in FIG. 4 or the like has a cylindrical shape having a uniform inner diameter, it may be shown in FIG. 5 or 6 below.
  • FIG. 5 is a diagram showing a modified example 1 of the spring guide of the rotary compressor according to the first embodiment.
  • FIG. 6 is a diagram showing a modified example 2 of the spring guide of the rotary compressor according to the first embodiment.
  • the inner diameter D2 of the portion (hereinafter referred to as the non-fixed portion) 32b other than the portion (hereinafter referred to as the fixed portion) 32a to which the large diameter portion 15b of the vane spring 15 is fixed is fixed. It is configured to be wider than the inner diameter D3 of the portion 32a. According to this configuration, the clearance between the outer peripheral surface of the small diameter portion 15a of the vane spring 15 and the inner peripheral surface of the non-fixed portion 32b of the spring guide 30 can be secured wider than that of the configuration of FIG. Therefore, the accuracy of the coaxiality between the vane spring 15 and the spring guide 30, which is required at the time of press fitting, can be relaxed.
  • the vane spring 15 must be inserted into the spring guide 30 while ensuring the coaxiality between the vane spring 15 and the spring guide 30, or the vane spring 15 will be inserted into the inner peripheral surface of the spring guide 30. It may be difficult to insert or it may not be possible to insert it.
  • the vane spring is provided by ensuring a wide clearance between the outer peripheral surface of the small diameter portion 15a of the vane spring 15 and the inner peripheral surface of the non-fixed portion 32b of the spring guide 30. Since the 15 can be easily inserted into the spring guide 30, the accuracy of the coaxiality between the vane spring 15 and the spring guide 30 can be relaxed.
  • the inner peripheral surface of the spring guide 30 may be provided with an inclined surface 33 that smoothly connects the inner peripheral surface of the fixed portion 32a and the inner peripheral surface of the non-fixed portion 32b.
  • the rigidity of the spring guide 30 can be improved.
  • the protrusion 6 is joined to an integral body in which an upper bearing 18, two cylinders 11, an intermediate plate 12, a lower bearing 19, and a rotating shaft 17 having two rolling pistons 13 are combined. It is fixed inside the closed container 5.
  • Each cylinder 11 is fixed to the closed container 5 at a position where the vane groove 22 faces the opening 8 of the closed container 5.
  • the vane 14 is inserted into the vane groove 22 of one of the two cylinders 11 fixed to the closed container 5.
  • the spring guide 30 is joined to the cylinder 11, and the vane spring 15 is inserted into and fixed to the spring guide 30.
  • 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.
  • the vane spring 15 was fixed to the spring guide 30 after the spring guide 30 was attached to the cylinder 11, but the reverse may be applied. That is, after fixing the vane spring 15 to the spring guide 30, the spring guide 30 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 rotary compressor 1 of the first embodiment is a rolling compressor that eccentrically rotates along a closed container 5, an annular cylinder 11 housed in the closed container 5, and an inner peripheral surface 11b of the cylinder 11. It includes a piston 13 and a vane 14 that reciprocates in a vane groove 22 provided in the cylinder 11 in the radial direction.
  • the rotary compressor 1 is a coil spring that urges the vane 14 to bring the tip portion 14a of the vane 14 into contact with the rolling piston 13, and is a large diameter portion having a diameter larger than that of the small diameter portion 15a and the small diameter portion 15a.
  • a vane spring 15 having the vane spring 15 and a spring guide 30 in which the large diameter portion 15b of the vane spring 15 comes into contact with the inner surface to fix the vane spring 15 are provided.
  • One end of the spring guide 30 is inserted into the closed container 5 through an opening 8 formed in the closed container 5, and is fixed to 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 more accurately on the cylinder 11.
  • the vane spring 15 is fixed by press-fitting a large diameter portion 15b into the spring guide 30.
  • the vane spring 15 can be fixed to the spring guide 30 by press-fitting the large diameter portion 15b.
  • the spring guide 30 is configured such that the inner diameter of the non-fixed portion 32b is larger than the inner diameter of the fixed portion 32a.
  • FIG. 7 is an explanatory view of a fixed structure of the vane spring and the spring guide in the rotary compressor according to the second embodiment.
  • the vane spring 15 is fixed to the spring guide 30A by using a screw fixing method.
  • the cylindrical spring guide 30A of the second embodiment has a thread groove 34 on the inner peripheral surface of the end portion on the rear end side in the screw insertion direction.
  • the thread groove 34 is a spiral groove.
  • the vane spring 15 is fixed in the spring guide 30A by screwing the large diameter portion 15b of the vane spring 15 into the thread groove 34.
  • the large diameter portion 15b of the vane spring 15 is attached so as to be guided along the screw groove 34 of the spring guide 30A. Therefore, the accuracy of the mounting position and posture of the vane spring 15 can be improved.
  • the spring force of the vane spring 15 that expands and contracts according to the movement of the vane 14, the inertial force of the vane spring 15 itself, and the vibration of the rotary compressor 1 are applied to the vane spring 15. And the force of.
  • the position of the vane spring 15 may deviate from the initial fixed position due to these forces. Therefore, it is necessary to design the thread groove 34 of the spring guide 30A and the large diameter portion 15b of the vane spring 15 in a shape and dimensions that can secure a holding force that does not shift the position of the vane spring 15.
  • the cross-sectional shape of the thread groove 34 is a semicircle along the wire rod of the vane spring 15, and the diameter of the semicircle is set to a diameter that matches the wire diameter of the vane spring 15.
  • the diameter matching the wire diameter of the vane spring 15 includes a diameter that matches the wire diameter of the vane spring 15 or is slightly smaller than the wire diameter of the vane spring 15.
  • the spring guide 30A of the rotary compressor 1 of the second embodiment has a thread groove 34 on the inner peripheral surface. Then, the large diameter portion 15b of the spring guide 30A is screwed into the screw groove 34, and the vane spring 15 is fixed to the spring guide.
  • the cross-sectional shape of the thread groove 34 is formed by a semicircle, and the diameter of the semicircle has a diameter that matches the wire diameter of the vane spring 15.
  • the method of fixing the vane spring 15 to the spring guide 30B is different from that of the first embodiment.
  • the fixing method of the third embodiment is a groove fixing method.
  • the differences between the third embodiment and the first embodiment will be mainly described, and the configurations not described in the third embodiment are the same as those in the first embodiment.
  • FIG. 8 is an explanatory view of a fixed structure of the vane spring and the spring guide in the rotary compressor according to the third embodiment.
  • the groove fixing method is used for fixing the vane spring 15 to the spring guide 30B.
  • the cylindrical spring guide 30B of the third embodiment has a circumferential groove 35 having a rectangular cross section on the inner peripheral surface. Then, the large diameter portion 15b of the vane spring 15 is fitted into the groove portion 35 and press-fitted, so that the vane spring 15 is fixed in the spring guide 30B.
  • the cross-sectional shape is not limited to a rectangular shape, and can be configured into any shape.
  • the spring force of the vane spring 15 that expands and contracts according to the movement of the vane 14, the inertial force of the vane spring 15 itself, and the vibration of the rotary compressor 1 are applied to the vane spring 15. With the force of. In addition to these forces, a frictional force due to contact with the inner peripheral surface of the spring guide 30B is further applied to the vane spring 15. The resultant force considering the direction of these forces acts in the direction of shifting the position of the vane spring 15. Therefore, if the operation is continued, the position of the vane spring 15 may deviate from the initial fixed position.
  • the vane spring 15 is fixed to the spring guide 30B with a holding force that does not shift the fixed position.
  • the press-fitting allowance of the large diameter portion 15b with respect to the groove portion 35 is set as follows.
  • the press-fitting allowance is the spring force of the vane spring 15 when the rolling piston 13 is located in the vane groove phase, that is, when the vane 14 is in the top dead center position, and the large diameter portion 15b of the vane spring 15 has a diameter of the groove portion 35. It is more than the press-fitting allowance that slides outward in the direction. Further, the press-fitting allowance is such that when the rolling piston 13 is positioned 180 ° different from the vane groove phase, that is, when the vane 14 is at the bottom dead center position, the large diameter portion 15b is the groove portion due to the inertial force of the vane spring 15 itself. It is less than the press-fitting allowance that does not slip on 35.
  • FIG. 8 shows a configuration in which the large-diameter portion 15b of the vane spring 15 is fitted into the groove portion 35 and press-fitted so that the vane spring 15 is fixed in the spring guide 30B. It may be configured as follows.
  • FIG. 9 is an explanatory view of a modified example of the fixed structure of the vane spring and the spring guide in the rotary compressor according to the third embodiment.
  • an intermediate diameter portion 15c having a diameter larger than that of the small diameter portion 15a and a smaller diameter than that of the large diameter portion 15b is provided between the small diameter portion 15a and the large diameter portion 15b.
  • the intermediate diameter portion 15c is press-fitted into the inner peripheral surface of the spring guide 30B.
  • the vane spring 15 is fixed in the spring guide 30B at both the large diameter portion 15b and the intermediate diameter portion 15c, so that the holding force can be further increased and the misalignment prevention effect can be enhanced. ..
  • a positioning portion composed of a non-expandable portion having a larger diameter is provided on the outer side in the radial direction of the large diameter portion 15b of the vane spring 15 shown in FIG. It can also be seen as a configuration that fits inside.
  • the spring guide 30B of the rotary compressor 1 of the third embodiment has a circumferential groove 35 on the inner peripheral surface, and the large diameter portion 15b of the vane spring 15 is fitted into the groove 35 to spring the vane spring 15. It is fixed to the guide.
  • the large diameter portion 15b of the vane spring 15 can be fitted and fixed in the circumferential groove portion 35 formed on the inner peripheral surface of the spring guide 30B.
  • the vane 14 reciprocates between the front bottom dead center position in the direction toward the center of the cylinder 11 and the rear top dead center position in the direction away from the cylinder 11.
  • the vane spring 15 has a large diameter portion 15b fitted into the groove portion 35 and press-fitted.
  • the press-fitting allowance for the groove portion 35 of the large-diameter portion 15b is the press-fitting allowance in which the large-diameter portion 15b of the vane spring 15 slides outward in the radial direction due to the spring force of the vane spring 15 when the rolling piston 13 is positioned in the vane groove phase.
  • the large diameter portion 15b of the vane spring 15 is set to be equal to or less than the press-fitting allowance that does not slip in the groove portion 35 due to the inertial force of the vane spring itself when the rolling piston 13 is located in a phase different from the vane groove phase by 180 °. ..
  • FIG. 10 is an explanatory view of a fixed structure of a vane spring and a spring guide in the rotary compressor according to the fourth embodiment.
  • the lid fixing method is used to fix the vane spring 15 to the spring guide 30C.
  • the inner diameter of the spring guide 30 is formed to be smaller than the outer diameter of the large diameter portion 15b of the vane spring 15, and the large diameter portion 15b is press-fitted into the spring guide 30 and fixed.
  • the inner diameter of the spring guide 30C is formed to be larger than the outer diameter of the large diameter portion 15b of the vane spring 15, and the entire vane spring 15 including the large diameter portion 15b comes into contact with the spring guide 30C. Not.
  • the spring guide 30C of the fourth embodiment has a cylindrical portion 36 and a spring lid 37 that closes the end portion of the cylindrical portion 36.
  • the vane spring 15 is always fixed between the vane 14 and the spring lid 37 in a state of being shrunk from the natural length. In this way, the vane spring 15 is arranged in the spring guide 30C in a contracted state, and the vane spring 15 is fixed in the spring guide 30C.
  • the protrusion 6 is joined to an integral body in which an upper bearing 18, two cylinders 11, an intermediate plate 12, a lower bearing 19, and a rotating shaft 17 having two rolling pistons 13 are combined. It is fixed inside 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.
  • the vane 14 is inserted into the vane groove 22 of one of the two cylinders 11 fixed to the closed container 5 from the open end of the protrusion 6.
  • the spring guide 30C is inserted from the open end of the protrusion 6 and the end is fixed to the fixing recess 40 of the cylinder 11.
  • the vane spring 15 is inserted into the spring guide 30C and fixed.
  • the vane 14, the spring guide 30C, 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.
  • the vane spring 15 was fixed to the spring guide 30 after the spring guide 30 was attached to the cylinder 11, but the reverse may be applied. That is, after fixing the vane spring 15 to the spring guide 30, the spring guide 30 may be attached to the cylinder 11.
  • the spring guide 30 has a cylindrical portion 36 and a spring lid 37 that closes the end portion of the cylindrical portion 36.
  • the vane spring 15 is always fixed between the vane 14 and the spring lid 37 in a state of being shrunk from the natural length. In this way, the vane spring 15 may be fixed in the spring guide 30.
  • the fifth embodiment relates to a refrigeration cycle apparatus including the rotary compressor 1 according to any one of the first to fourth embodiments.
  • FIG. 11 is a diagram showing a refrigerant circuit of the refrigeration cycle device according to the fifth embodiment. It includes a refrigeration cycle device 50, a rotary compressor 1 according to any one of the first to fourth embodiments, 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
  • the refrigeration cycle device 50 configured in this way is provided with the rotary compressor 1 according to any one of the first to fourth embodiments, 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 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/JP2019/045599 2019-11-21 2019-11-21 回転式圧縮機および冷凍サイクル装置 Ceased WO2021100167A1 (ja)

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JP2021558114A JP7275311B2 (ja) 2019-11-21 2019-11-21 回転式圧縮機および冷凍サイクル装置
PCT/JP2019/045599 WO2021100167A1 (ja) 2019-11-21 2019-11-21 回転式圧縮機および冷凍サイクル装置
CN201980102291.6A CN114729640B (zh) 2019-11-21 2019-11-21 旋转式压缩机以及制冷循环装置
CZ2022-182A CZ2022182A3 (cs) 2019-11-21 2019-11-21 Rotační kompresor a zařízení chladicího cyklu

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CZ2022182A3 (cs) 2022-05-25
CN114729640A (zh) 2022-07-08

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