WO2022009267A1 - ロータリ圧縮機 - Google Patents

ロータリ圧縮機 Download PDF

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Publication number
WO2022009267A1
WO2022009267A1 PCT/JP2020/026414 JP2020026414W WO2022009267A1 WO 2022009267 A1 WO2022009267 A1 WO 2022009267A1 JP 2020026414 W JP2020026414 W JP 2020026414W WO 2022009267 A1 WO2022009267 A1 WO 2022009267A1
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WO
WIPO (PCT)
Prior art keywords
compression
piston
rotary
eccentric
cylinder
Prior art date
Application number
PCT/JP2020/026414
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
祐策 石部
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2022534499A priority Critical patent/JP7325644B2/ja
Priority to PCT/JP2020/026414 priority patent/WO2022009267A1/ja
Priority to CN202080102248.2A priority patent/CN115917154A/zh
Publication of WO2022009267A1 publication Critical patent/WO2022009267A1/ja

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    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation

Definitions

  • This disclosure relates to a rotary compressor having an injection mechanism.
  • the conventional rotary compressor has a configuration in which a compression mechanism unit and an electric motor unit that drives the compression mechanism unit via a rotating shaft are arranged in a closed container.
  • the compression mechanism mainly includes a cylindrical cylinder, a rotary piston rotatably mounted on the eccentric shaft of the rotary shaft, and vanes slidably arranged in a vane groove provided in the cylinder.
  • a through hole is formed in the substantially center of the cylinder in the axial direction, and a cylinder chamber is formed in the cylinder by closing the through hole with end plates arranged on both end faces in the axial direction of the cylinder. ..
  • a compression chamber partitioned by vanes is formed in the cylinder chamber, and the rotating shaft rotates and the rotating piston rotates eccentrically in the cylinder chamber, so that the volume of the compression chamber is reduced and the refrigerant is compressed. It has become.
  • the injection port may be located inside the inner peripheral surface of the rotating piston in the process of eccentric rotation of the rotating piston. Since there is a vacant space inside the inner peripheral surface of the rotating piston where refrigerating machine oil collects, if the injection port is located inside the inner peripheral surface of the rotating piston and faces this vacant space, the injection refrigerant Problems such as backflow and discharge of refrigerating machine oil occur.
  • an annular seal portion protruding inward in the radial direction is integrally provided on the rotary piston on the contact surface side with the end plate of the rotary piston. This sealing portion closes the portion of the injection port located inside the inner peripheral surface of the rotating piston regardless of the position of the rotating phase, and the injection port is an empty space inside the inner peripheral surface of the rotating piston. I was trying not to face.
  • Patent Document 1 it is possible to prevent the injection port from facing the above-mentioned vacant space by providing an annular seal portion on the rotating piston, but on the other hand, there are the following problems. That is, by providing the seal portion, a gap of at least the radial thickness of the seal portion is created between the spindle portion of the rotating shaft passed inside the seal portion and the rotary piston, and the amount of eccentricity is expanded to the maximum. There is a problem that it cannot be done and the amount of eccentricity is limited.
  • This disclosure has been made in view of these points, and it is possible to maximize the amount of eccentricity of the eccentric shaft portion of the rotating shaft while having a structure that prevents the injection port from facing the inside of the rotating piston.
  • the purpose is to provide a rotary compressor.
  • the rotary compressor according to the present disclosure is a rotary compressor including a compression mechanism unit that compresses the refrigerant in the compression chamber, and the intermediate pressure refrigerant is injected into the compression chamber of the compression mechanism unit from the injection port.
  • a rotary shaft having a spindle and an eccentric shaft, a cylinder having a cylinder chamber, a rotary piston mounted on the eccentric shaft of the rotary shaft and rotating eccentrically in the cylinder chamber, and an axial direction of the rotary shaft in the cylinder.
  • It is equipped with a seal plate that closes the portion of the injection port formed on one end plate of the plate that is located inside the inner peripheral surface of the rotating piston, and the seal plate is separate from the rotating piston and rotates. It is relatively rotatable with respect to the piston, has a through hole through which the main shaft portion of the rotating shaft is passed, and the through hole is open to the outside in the radial direction.
  • the rotary compressor of the present disclosure has a seal plate that closes a portion of the injection port located inside the inner peripheral surface of the rotary piston, and has a structure that prevents the injection port from facing the inside of the rotary piston. ing.
  • the seal plate is separate from the rotary piston and is rotatable with respect to the rotary piston, has a through hole through which the main shaft portion of the rotary shaft is passed, and the through hole is opened radially outward. .. Since the through hole is opened to the outside in the radial direction in this way, the main shaft portion of the rotating shaft can be arranged closer to the open side of the through hole, and the eccentric shaft portion can be arranged according to the position of the main shaft portion of the rotating shaft in the through hole.
  • the amount of eccentricity can be adjusted. Therefore, when the spindle portion is moved toward the open side of the through hole until it comes into contact with the inner peripheral surface of the rotary piston, the amount of eccentricity of the eccentric shaft portion of the rotary shaft can be expanded to the maximum.
  • FIG. It is a partially enlarged view of FIG. It is explanatory drawing of the eccentric amount of the eccentric shaft part in the rotary compressor which concerns on this embodiment. It is a partially enlarged view of FIG. It is explanatory drawing of the assembly process in the twin rotary compressor of a conventional structure. It is explanatory drawing of the assembly process in the twin rotary compressor of a conventional structure. It is explanatory drawing of the assembly process in the rotary compressor which concerns on embodiment. It is a figure which shows the modification 1 of the rotary compressor which concerns on embodiment. It is a figure which shows the modification 2 of the rotary compressor which concerns on embodiment. It is a figure which shows the modification 3 of the rotary compressor which concerns on embodiment.
  • FIG. 1 is a schematic cross-sectional view of a rotary compressor according to an embodiment.
  • FIG. 2 is a schematic cross-sectional view of the compression mechanism portion cut along the line AA of FIG.
  • the rotary compressor of FIG. 1 is a rotary compressor with an injection mechanism.
  • the rotary compressor has a configuration in which a compression mechanism unit 2, an electric motor unit 3, and a rotating shaft 4 for transmitting the driving force of the electric motor unit 3 to the compression mechanism unit 2 are arranged in a closed container 1.
  • a twin rotary type rotary compressor in which the compression mechanism unit 2 has two cylinders will be described as an example, but the present invention is not limited to this, and one or more cylinders may be used.
  • the longitudinal direction of the closed container 1 (vertical direction in the figure), the direction in which the rotation axis 4 extends is the axial direction, the direction perpendicular to the axis direction is the radial direction, and the direction around the rotation axis 4 is defined as the axial direction. It is called the circumferential direction.
  • the rotating shaft 4 is rotated by the motor unit 3 and the compression mechanism unit 2 is driven to compress the refrigerant.
  • the refrigerant is sucked into the closed container 1 through the suction muffler 8, compressed by the compression mechanism 2, and then turned into a high-temperature and high-pressure gas and discharged into the closed container 1.
  • the refrigerant gas discharged into the closed container 1 passes through the gap of the motor unit 3 and is discharged from the discharge pipe 5 into the refrigerant circuit.
  • the lower part of the closed container 1 is an oil pool in which refrigerating machine oil is collected.
  • the refrigerating machine oil in the oil sump is sucked up from a hollow hole provided in the axial direction of the rotating shaft 4 in the same manner as a centrifugal pump using the rotation of the rotating shaft 4, and the sucked up refrigerating machine oil is sucked up from the hollow hole to the outer peripheral portion. It is supplied to each sliding portion through a lubrication hole extending toward the sliding portion.
  • the seal with refrigerating machine oil also plays a role in preventing the leakage of the refrigerant.
  • the rotating shaft 4 has a spindle portion 4a and an eccentric shaft portion 4b eccentric with respect to the axis of the spindle portion 4a. Two eccentric shaft portions 4b are provided in the same number as the number of cylinders.
  • An oil separator 6 that separates the refrigerant and the refrigerating machine oil is fitted in the upper part of the rotating shaft 4.
  • the oil separator 6 is formed in a disk shape, and is installed at a position where the mixed fluid of the refrigerant flowing from the compression mechanism unit 2 toward the discharge pipe 5 and the refrigerating machine oil collides with each other. When the mixed fluid collides with the oil separator 6, the refrigerant and the refrigerating machine oil are separated.
  • the oil separator 6 By separating the refrigerant and the refrigerating machine oil by the oil separator 6, it is possible to prevent the refrigerating machine oil from being discharged from the discharge pipe 5 to the outside of the compressor together with the refrigerant discharged from the compression mechanism unit 2. As a result, seizure of the sliding portion due to the depletion of the oil in the closed container 1 is prevented.
  • the motor unit 3 includes a stator 3a and a rotor 3b.
  • a rotation shaft 4 is fixed to the rotor 3b, and the rotation of the rotor 3b causes the rotation shaft 4 to rotate, so that rotational power is transmitted to the compression mechanism unit 2.
  • the compression mechanism unit 2 includes a first compression unit 20A, a second compression unit 20B, an upper bearing 10 arranged on the upper end surface of the first compression unit 20A, and a lower surface arranged on the lower end surface of the second compression unit 20B. It includes a bearing 11 and an intermediate plate 12. The end of the injection pipe 7 that penetrates the closed container 1 from the outside is connected to the intermediate plate 12.
  • the first compression unit 20A and the second compression unit 20B are not distinguished, they may be collectively referred to as the compression unit 20.
  • the upper bearing 10 has a hollow cylindrical bearing portion 10a that rotatably supports the rotating shaft 4, and a flat plate annular end plate 10b that closes the upper end surface of the cylinder 21 described later.
  • the lower bearing 11 has a hollow cylindrical bearing portion 11a that rotatably supports the rotating shaft 4, and a flat plate annular end plate 11b that closes the lower end surface of the cylinder 21 described later.
  • Discharge ports are formed on the end plate 10b of the upper bearing 10 and the end plate 10b of the lower bearing 11.
  • An upper discharge muffler 13 and a lower discharge muffler 14 are installed so as to cover the discharge port.
  • the upper discharge muffler 13 and the lower discharge muffler 14 reduce the noise amplified by the resonance of the inner space of the closed container 1.
  • first compression unit 20A and the second compression unit 20B of the compression mechanism unit 2 will be described. Since the first compression unit 20A and the second compression unit 20B have basically the same configuration, the first compression unit 20A will be described below as a representative.
  • the first compression portion 20A is rotatably mounted on a cylindrical cylinder 21 having a through hole penetrating in the axial direction (vertical direction in FIG. 1) and an eccentric shaft portion 4b of the rotary shaft 4, and rotates eccentric in the cylinder chamber. It is provided with a rotating piston 22 and a vane 23.
  • the first compression unit 20A further includes a seal plate 40 that is separate from the rotary piston 22.
  • An upper bearing 10 and an intermediate plate 12 are arranged on both end faces in the axial direction of the cylinder 21.
  • the through hole of the cylinder 21 is closed by the end plate 10b of the upper bearing 10 and the intermediate plate 12, so that the cylinder chamber 24 is formed in the cylinder 21. In this way, the end plate 10b and the intermediate plate 12 of the upper bearing 10 function as end plates for closing the through holes.
  • a vane groove 23a extending in the radial direction is formed in the cylinder 21, and the vane 23 is slidably arranged in the vane groove 23a.
  • the vane 23 projects into the cylinder chamber 24, and the tip of the vane 23 comes into contact with the rotary piston 22 to partition the inside of the cylinder chamber 24 into a suction chamber 24a and a compression chamber 24b.
  • a suction port 26 communicating with the suction chamber 24a is formed on the inner peripheral surface 22c of the cylinder 21, and the refrigerant from the suction muffler 8 is guided to the suction chamber 24a via the suction port 26. Further, a discharge port 27 communicating with the compression chamber 24b is formed on the inner peripheral surface 22c of the cylinder 21, and the refrigerant compressed to the discharge pressure in the compression chamber 24b is discharged from the discharge port 27.
  • the compression mechanism unit 2 further includes an injection flow path 30 that guides an injection refrigerant, which is an intermediate pressure liquid refrigerant or a gas refrigerant, to the compression chamber 24b.
  • the injection flow path 30 is formed in the intermediate plate 12.
  • the injection flow path 30 is a flow path for introducing the injection refrigerant into each of the compression chamber 24b of the first compression unit 20A and the compression chamber 24b of the second compression unit 20B.
  • the injection port 30a which is the downstream end of the injection flow path 30, is open to the upper and lower end surfaces of the intermediate plate 12.
  • the injection refrigerant flowing into the injection flow path 30 from the outside is introduced from each injection port 30a into the compression chamber 24b of the first compression unit 20A and the compression chamber 24b of the second compression unit 20B, respectively. Further, a vacant space 50 in which the refrigerating machine oil and the refrigerant are collected is provided on the inner peripheral side of the rotary piston 22 and at the stepped portion between the spindle portion 4a and the eccentric shaft portion 4b.
  • the rotating shaft 4 fixed to the rotor 3b rotates, and the refrigerant is sucked from the refrigerant circuit into the suction chamber 24a in the cylinder 21 through the suction muffler 8 through the suction port 26. Will be done.
  • the refrigerant sucked into the suction chamber 24a is compressed by the eccentric rotational movement of the rotary piston 22.
  • the compressed and high pressure refrigerant is discharged from the compression chamber 24b into the closed container 1 through the discharge port 27 and the discharge port (not shown) formed in the upper bearing 10.
  • the refrigerant gas discharged into the closed container 1 passes through the discharge pipe 5 and is discharged to the refrigerant circuit outside the compressor.
  • the injection refrigerant flowing into the injection pipe 7 from the external refrigerant circuit is injected into the cylinder chamber 24 from the injection port 30a via the injection flow path 30.
  • the injection of the injection refrigerant into the cylinder chamber 24 is performed when the injection port 30a faces the cylinder chamber 24.
  • the injection of the injection refrigerant into the cylinder chamber 24 is performed within a range of a specific rotation phase according to the position of the injection port 30a during one rotation of the rotary piston 22.
  • the following is a structure for preventing the injection port from facing an empty space inside the inner peripheral surface of the rotating piston.
  • the structure of is working. That is, on the contact surface side of the rotary piston with the injection port, an annular seal portion protruding inward in the radial direction is integrally provided with respect to the rotary piston.
  • this structure which will be described below with reference to the figure, the amount of eccentricity of the eccentric shaft portion is limited, and the amount of eccentricity cannot be expanded to the maximum.
  • the eccentric shaft portion is prevented from facing the vacant space 50 (see FIG. 1) inside the inner peripheral surface 22c of the rotary piston 22. It is possible to expand the amount of eccentricity of 4b to the maximum.
  • the configuration and operation of the seal plate 40 will be described first, and then the point that the eccentric amount of the eccentric shaft portion 4b can be expanded to the maximum will be described.
  • FIG. 3 is a diagram showing a seal plate of the rotary compressor according to the embodiment.
  • FIG. 3A is a plan view
  • FIG. 3B is a cross-sectional view.
  • FIG. 4 is an explanatory view of the arrangement portion of the seal plate of FIG. 3, and is a diagram showing a rotating piston of the first compression portion. 4 (a) is a plan view
  • FIG. 4 (b) is a cross-sectional view.
  • FIG. 5 is a diagram showing a state in which the seal plate of FIG. 3 is arranged on the rotary piston of FIG. 5 (a) is a plan view
  • FIG. 5 (b) is a cross-sectional view.
  • the seal plate portion is hatched in order to clearly indicate the position of the seal plate portion.
  • the seal plate 40 has a circular outer shape, has a through hole 41 through which the main shaft portion 4a of the rotating shaft 4 passes, and has a shape in which the through hole 41 is open to the outside in the radial direction. In other words, the seal plate 40 has a shape in which a part of the annular member is cut out.
  • an annular recess 22b coaxial with the rotary piston 22 is formed on the end face 22a on the injection port 30a side of both end faces in the axial direction of the rotary piston 22.
  • the seal plate 40 is rotatably arranged in the recess 22b.
  • the seal plate 40 is in contact with the intermediate plate 12 in a state of being arranged in the recess 22b.
  • the seal plate 40 has a portion protruding inward from the inner peripheral surface 22c of the rotary piston 22, and the portion located inside the inner peripheral surface 22c of the rotary piston 22 in the injection port 30a by this protruding portion. To block.
  • the spindle portion 4a of the rotary shaft 4 passes through the through hole 41 at a position closer to the open side of the through hole 41 of the seal plate 40 than the central shaft O of the rotary piston 22.
  • the seal plate 40 is rotatably arranged in the recess 22b, it does not make one rotation in the recess 22b.
  • the linear inner surface 41a on the open side of the through hole 41 comes into contact with the outer peripheral surface of the main shaft portion 4a, so that the rotation range of the seal plate 40 is adjusted. ..
  • the purpose of adjusting the rotation range is to adjust the posture of the seal plate 40 at the time of eccentric rotation of the rotating piston 22, and this point will be described with reference to FIG. 6 below.
  • FIG. 6 is a diagram showing a compression operation of the rotary compressor according to the embodiment, and is a schematic cross-sectional view of a compression mechanism portion cut along the line AA of FIG.
  • FIG. 6 shows how the rotation phase of the rotation shaft 4 advances to 0 °, 90 °, 180 °, 270 °, and the rotation piston 22 makes an eccentric rotational movement while contacting the inner peripheral surface of the cylinder 21.
  • the seal plate 40 is also eccentrically rotating in conjunction with the eccentric rotation of the rotating piston 22.
  • the seal plate 40 is rotatable relative to the rotary piston 22, but its rotation range is adjusted. Therefore, in the seal plate 40, the rotary piston 22 keeps the posture in which the open side of the through hole 41 faces the side opposite to the eccentric direction of the eccentric shaft portion 4b (not shown in FIG. 6, see FIG. 5 and the like). It is linked to the eccentric rotation of. Specifically, when the rotation phase is 0 °, the open side of the through hole 41 is in a downward posture on the paper surface of FIG. 6, in other words, the open side of the through hole 41 is in the eccentric direction of the eccentric shaft portion 4b. It is in a posture facing the opposite side to the upper side on the paper surface of FIG.
  • the posture is 90 ° counterclockwise from the posture when the rotation phase is 0 °.
  • the posture of the seal plate 40 changes to the posture of rotating counterclockwise by 90 ° as the phase advances with the rotation phase of 180 ° and the rotation phase of 270 °.
  • the injection port 30a faces the suction chamber 24a immediately after the completion of suction.
  • the injection port 30a faces the compression chamber 24b, and a part of the injection port 30a is blocked by the rotation piston 22.
  • the rotation phase is 180 °, the injection port 30a faces the inside of the inner peripheral surface 22c of the rotation piston 22.
  • the injection port 30a is closed by the seal plate 40. That is, even if the injection port 30a is located inside the inner peripheral surface 22c of the rotary piston 22, it can be closed by the seal plate 40.
  • the rotation phase is 270 °, the injection port 30a is blocked by the rotation piston 22 itself.
  • the injection port 30a can be closed by the seal plate 40 even when the injection port 30a is located inside the inner peripheral surface 22c of the rotary piston 22. .. Therefore, it is possible to suppress performance deterioration due to the injection refrigerant not flowing into the cylinder chamber 24 at the time of injection but flowing into the vacant space 50 (see FIG. 1). At the same time, it is possible to suppress the deterioration of reliability due to the injection refrigerant blowing off the refrigerating machine oil stored in the vacant space 50 and reducing the lubrication capacity. Further, even when the injection is not performed, the refrigerating machine oil stored in the vacant space 50 can be suppressed from flowing out to the injection flow path 30 via the injection port 30a, and the deterioration of reliability can be suppressed.
  • the seal plate 40 it is possible to avoid communication between the injection port 30a and the inside of the inner peripheral surface 22c of the rotary piston 22 regardless of the size of the injection port 30a. Therefore, the diameter of the injection port 30a can be increased, and the injection amount can be increased.
  • FIG. 7 is an explanatory diagram of an area in which an injection port can be arranged in the rotary compressor according to the embodiment.
  • the annular region 60 shown by hatching is a region in which the injection port 30a faces inward from the inner peripheral surface 22c of the rotary piston 22 while the rotary piston 22 makes an eccentric rotary motion. Therefore, in the case of a structure in which the seal plate 40 is not provided, it is necessary to arrange the injection port 30a while avoiding the annular region 60. Specifically, it is necessary to arrange the injection port 30a in a region outside the outer circumference of the annular region 60. Since the region inside the inner circumference of the annular region 60 is a region blocked by the rotary piston 22 in the entire rotation phase, the injection port 30a cannot be arranged.
  • the seal plate 40 by providing the seal plate 40, even if the injection port 30a is located in the annular region 60, the injection port 30a can be closed by the seal plate 40. Therefore, the annular region 60 is also included in the region where the injection port 30a can be arranged, and the degree of freedom in designing the arrangement position of the injection port 30a is improved.
  • FIG. 8 is an explanatory diagram of the amount of eccentricity of the eccentric shaft portion of the conventional structure.
  • FIG. 8 shows an example in which the conventional structure is applied to a rotary compressor provided with two cylinders.
  • FIG. 9 is a partially enlarged view of FIG.
  • FIG. 10 is an explanatory diagram of the amount of eccentricity of the eccentric shaft portion in the rotary compressor according to the present embodiment.
  • FIG. 11 is a partially enlarged view of FIG.
  • an annular seal portion 140 projecting inward in the radial direction is integrally provided at the end portion of the rotary piston 122 on the injection port 130a side.
  • the seal portion 140 circles in an annular shape without a break, and has a radial thickness w over the entire circumferential direction as shown in FIG. Since the rotary shaft 104 passes through the inside of the annular seal portion 140, a gap of at least the thickness w of the seal portion is formed between the outer peripheral surface 104aa of the main shaft portion 104a and the inner peripheral surface 122a of the rotary piston 122.
  • the eccentric shaft portion 104b is arranged so as to fill the gap.
  • the distance between the inner peripheral surface 122a of the rotary piston 122 and the outer peripheral surface 104aa of the spindle portion 104a on the eccentric side of the eccentric shaft portion 104b is ⁇ .
  • the through hole 41 through which the main shaft portion 4a of the rotating shaft 4 is passed is opened to the outside in the radial direction in the seal plate 40. Therefore, the spindle portion 4a of the rotary shaft 4 can be arranged closer to the open side of the through hole 41 to a position where it contacts the inner peripheral surface 22c of the rotary piston 22. Therefore, it is not necessary to secure the w portion of the eccentric shaft portion on the side opposite to the eccentric side, which is necessary in the conventional structure. Therefore, as shown in FIGS.
  • the radial end of the spindle portion 4a and the radial end of the eccentric shaft portion 4b are flush with each other, and the outer peripheral surface 4aa of the spindle portion 4a and the inside of the rotary piston 22 are aligned. It can be configured in a state where it is in contact with the peripheral surface 22c.
  • the distance ⁇ between the inner peripheral surface 22c of the rotary piston 22 and the outer peripheral surface 4aa of the spindle portion 4a on the eccentric side (left side of FIG. 11) of the eccentric shaft portion 4b is set in the conventional structure. It can be made larger than the distance ⁇ , and the eccentric amount of the eccentric shaft portion 4b can be expanded to the maximum.
  • FIGS. 10 and 11 show a configuration in which the eccentric amount of the eccentric shaft portion 4b is expanded to the maximum, it is arbitrary whether or not the eccentric shaft portion 4b is expanded to the maximum.
  • the spindle portion 4a of the rotary shaft 4 can be arranged closer to the open side of the through hole 41, so that the spindle portion 4a of the rotary shaft 4 in the through hole 41 is eccentric according to the position of the spindle portion 4a.
  • the amount of eccentricity of the shaft portion 4b can be adjusted to the maximum.
  • the maximum eccentric amount of the structure of the present embodiment is the radius of the spindle portion 4a and the eccentric shaft portion. It corresponds to the difference from the radius of 4b. Therefore, according to the structure of the present embodiment, the eccentric shaft portion 4b of the rotating shaft 4 is placed from a position coaxial with the spindle portion 4a within a range equal to or less than the difference between the radius of the spindle portion 4a and the radius of the eccentric shaft portion 4b. , The configuration can be eccentric to the side opposite to the open side of the through hole 41.
  • the seal plate 40 of the present embodiment has a through hole 41 opened to the outside in the radial direction, and is not a closed annular shape but an annular shape partially cut out.
  • FIG. 12 is an explanatory diagram of an assembly process in a twin rotary compressor having a conventional structure, and is a diagram showing before installation of a rotary piston.
  • FIG. 13 is an explanatory diagram of an assembly process in a twin rotary compressor having a conventional structure, and is a diagram showing after the rotary piston is installed.
  • FIG. 14 is an explanatory diagram of an assembly process in the rotary compressor according to the embodiment.
  • the intermediate plate is not shown in FIGS. 12 to 14. Since the intermediate plate has an inner diameter larger than the outer diameter of the eccentric shaft portion, it may be installed inside the intermediate plate through the eccentric shaft portion. The intermediate plate may be installed at an arbitrary timing before installing the rotary piston on the eccentric shaft portion.
  • each rotary piston 122 is installed from both ends of the rotary shaft 104 having the two eccentric shaft portions 104b.
  • the inner diameter w1 of the seal portion 140 is smaller than the outer diameter w2 of the eccentric shaft portion 104b. Therefore, as shown in FIG. 13, each seal portion 140 cannot pass through each eccentric shaft portion 104b, and the rotary piston 22 cannot be installed on the outer periphery of the eccentric shaft portion 4b.
  • the seal plate 40 since the seal plate 40 has a through hole 41 and is an annular shape in which a part is cut out, the degree of freedom of installation is high and assembly is possible. That is, as shown in FIG. 14, the rotary shaft 4 having the two eccentric shaft portions 4b is installed in the recess 22b of the rotary piston 22 from the side of the rotary shaft 4 by using the through hole 41 of the seal plate 40. It can be assembled and is easy to assemble.
  • both of the two injection ports 30a are formed on the intermediate plate 12, but the configuration is not limited to this. Other configuration examples will be described with reference to FIGS. 15 to 17 below.
  • FIG. 15 is a diagram showing a modification 1 of the rotary compressor according to the embodiment.
  • FIG. 16 is a diagram showing a modification 2 of the rotary compressor according to the embodiment.
  • FIG. 17 is a diagram showing a modification 3 of the rotary compressor according to the embodiment.
  • the injection port 30a on the first compression portion 20A side is formed on the end plate 10b of the upper bearing 10
  • the injection port 30a on the second compression portion 20B side is formed on the end plate 11b of the lower bearing 11. May be.
  • the injection port 30a on the first compression portion 20A side is formed on the end plate 10b of the upper bearing 10 and the injection port 30a on the second compression portion 20B side is formed on the intermediate plate 12.
  • the injection port 30a on the first compression portion 20A side is formed on the intermediate plate 12, and the injection port 30a on the second compression portion 20B side is formed on the end plate 11b of the lower bearing 11. May be good.
  • the two injection ports 30a are either both formed in the intermediate plate 12, or are formed separately in the end plate 10b and the end plate 10b, or one is formed in one of the end plate 10b and the end plate 10b. The other may be formed on the intermediate plate 12.
  • the rotary compressor of the present embodiment includes a compression mechanism unit 2 that compresses the refrigerant in the compression chamber 24b, and an intermediate pressure refrigerant is supplied from the injection port 30a into the compression chamber 24b of the compression mechanism unit 2. It is a rotary compressor that is injected.
  • the compression mechanism portion 2 is mounted on a rotary shaft 4 having a spindle portion 4a and an eccentric shaft portion 4b, a cylinder 21 having a cylinder 21 chamber, and an eccentric shaft portion 4b of the rotary shaft 4, and rotates eccentrically in the cylinder 21 chamber.
  • a rotary piston 22 is provided.
  • the compression mechanism portion 2 projects into the cylinder 21 chamber of the cylinder 21 with the two end plates 10b and 11b arranged on both end faces of the rotary shaft 4 in the axial direction of the cylinder 21, and abuts on the rotary piston 22.
  • a vane 23 that forms a compression chamber 24b is provided in the cylinder 21 chamber.
  • the compression mechanism portion 2 is further linked to the eccentric rotation of the rotary piston 22 and is inside the inner peripheral surface 22c of the rotary piston 22 of the injection port 30a formed on one of the two end plates 10b.
  • a seal plate 40 for closing the located portion is provided.
  • the seal plate 40 is separate from the rotary piston 22 and is relatively rotatable with respect to the rotary piston 22, and has a through hole 41 through which the main shaft portion 4a of the rotary shaft 4 is passed. Is open to the outside in the radial direction.
  • the rotary compressor has a seal plate 40 that closes the portion of the injection port 30a located inside the inner peripheral surface of the rotary piston 22, and the injection port 30a faces the inside of the rotary piston 22.
  • the seal plate 40 is separate from the rotary piston 22 and is rotatable with respect to the rotary piston 22. It has a through hole 41 through which the main shaft portion 4a of the rotary shaft 4 is passed, and the through hole 41 has a diameter. It is open to the outside of the direction.
  • the spindle portion 4a of the rotary shaft 4 can be arranged closer to the open side of the through hole 41, and the position of the spindle portion 4a of the rotary shaft 4 in the through hole 41 can be arranged.
  • the amount of eccentricity of the eccentric shaft portion 4b can be adjusted accordingly. Therefore, when the spindle portion 4a is moved toward the open side of the through hole 41 until it comes into contact with the inner peripheral surface of the rotary piston 22, the amount of eccentricity of the eccentric shaft portion 4b of the rotary shaft 4 is expanded to the maximum. Is possible.
  • the spindle portion 4a of the rotary shaft 4 passes through the through hole 41 at a position closer to the open side of the through hole 41 of the seal plate 40 than the central axis of the rotary piston 22.
  • the eccentric shaft portion 4b of the rotating shaft 4 is located on the side opposite to the open side of the through hole 41 from the position coaxial with the spindle portion 4a within the range equal to or less than the difference between the radius of the spindle portion 4a and the radius of the eccentric shaft portion 4b. I'm eccentric.
  • the seal plate 40 is interlocked with the eccentric rotation of the rotary piston 22 while maintaining a posture in which the open side of the through hole 41 faces the side opposite to the eccentric direction of the eccentric shaft portion 4b.
  • the compression mechanism unit 2 includes two compression units including a cylinder 21, a rotary piston 22, and a vane 23 in the axial direction, and in addition to the two end plates 10b, yet another end plate.
  • An intermediate plate 12 is provided as 10b.
  • One side of the two compression units in the axial direction is the first compression unit 20A and the other side is the second compression unit 20B, one side in the axial direction of the first compression unit 20A and the axial direction of the second compression unit 20B.
  • An end plate 10b is arranged on each of the other sides of the above, and an intermediate plate 12 is arranged between the first compression portion 20A and the second compression portion 20B.
  • the two injection ports 30a for guiding the intermediate pressure refrigerant to the respective compression chambers 24b of the two compression mechanism portions 2 are formed on the intermediate plate 12 or separately on the two end plates 10b. One is formed on one of the two end plates 10b and the other is formed on the intermediate plate 12.
  • the compression mechanism unit 2 may be configured to include two compression units.
  • the positions of the injection ports 30a corresponding to each compression portion are either both formed on the intermediate plate 12 or divided into two end plates 10b, or one of the two end plates 10b. It suffices if it is formed on one side and the other side is formed on the intermediate plate 12.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2020/026414 2020-07-06 2020-07-06 ロータリ圧縮機 WO2022009267A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2022534499A JP7325644B2 (ja) 2020-07-06 2020-07-06 ロータリ圧縮機
PCT/JP2020/026414 WO2022009267A1 (ja) 2020-07-06 2020-07-06 ロータリ圧縮機
CN202080102248.2A CN115917154A (zh) 2020-07-06 2020-07-06 旋转式压缩机

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2020/026414 WO2022009267A1 (ja) 2020-07-06 2020-07-06 ロータリ圧縮機

Publications (1)

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WO2022009267A1 true WO2022009267A1 (ja) 2022-01-13

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Application Number Title Priority Date Filing Date
PCT/JP2020/026414 WO2022009267A1 (ja) 2020-07-06 2020-07-06 ロータリ圧縮機

Country Status (3)

Country Link
JP (1) JP7325644B2 (zh)
CN (1) CN115917154A (zh)
WO (1) WO2022009267A1 (zh)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6153489A (ja) * 1984-08-22 1986-03-17 Mitsubishi Electric Corp ロ−タリ−圧縮機
JPH0544670A (ja) * 1991-08-19 1993-02-23 Mitsubishi Heavy Ind Ltd ロータリ圧縮機
JPH1113664A (ja) * 1997-06-27 1999-01-19 Daikin Ind Ltd ロータリ圧縮機
JPH1193874A (ja) * 1997-09-18 1999-04-06 Daikin Ind Ltd ロータリ圧縮機

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6153489B2 (ja) 2014-03-27 2017-06-28 株式会社トクヤマ 結晶成長装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6153489A (ja) * 1984-08-22 1986-03-17 Mitsubishi Electric Corp ロ−タリ−圧縮機
JPH0544670A (ja) * 1991-08-19 1993-02-23 Mitsubishi Heavy Ind Ltd ロータリ圧縮機
JPH1113664A (ja) * 1997-06-27 1999-01-19 Daikin Ind Ltd ロータリ圧縮機
JPH1193874A (ja) * 1997-09-18 1999-04-06 Daikin Ind Ltd ロータリ圧縮機

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JP7325644B2 (ja) 2023-08-14
CN115917154A (zh) 2023-04-04
JPWO2022009267A1 (zh) 2022-01-13

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