WO2021100141A1 - スクロール圧縮機および冷凍サイクル装置 - Google Patents

スクロール圧縮機および冷凍サイクル装置 Download PDF

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Publication number
WO2021100141A1
WO2021100141A1 PCT/JP2019/045428 JP2019045428W WO2021100141A1 WO 2021100141 A1 WO2021100141 A1 WO 2021100141A1 JP 2019045428 W JP2019045428 W JP 2019045428W WO 2021100141 A1 WO2021100141 A1 WO 2021100141A1
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Prior art keywords
scroll
oscillating scroll
oscillating
guide
guide member
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Application number
PCT/JP2019/045428
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English (en)
French (fr)
Japanese (ja)
Inventor
角田　昌之
雷人 河村
渉 岩竹
佐々木　圭
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.)
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2021558092A priority Critical patent/JPWO2021100141A1/ja
Priority to PCT/JP2019/045428 priority patent/WO2021100141A1/ja
Publication of WO2021100141A1 publication Critical patent/WO2021100141A1/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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents

Definitions

  • the present invention relates to a scroll compressor used for an air conditioner, a refrigerator, etc., and a refrigerating cycle device.
  • the scroll compressor revolves the oscillating scroll with respect to the non-oscillating scroll to change the volume of a plurality of compression chambers composed of the non-oscillating scroll and the oscillating scroll from the outer side to the inner side.
  • the compression is performed by gradually decreasing toward.
  • the spiral tooth thermally expands in the axial direction as the temperature rises due to compression, so that the axial clearance between the preset spiral tooth tip and the tooth bottom becomes smaller. Therefore, under the conditions within the operating range, the oscillating scroll and the non-oscillating scroll are positioned in the axial direction so that the amount of thermal expansion does not exceed the set clearance. In order to reduce the leakage loss that increases due to the large tooth tip gap under operating conditions where the amount of thermal expansion is small, the tooth tips of the spiral teeth of the swing scroll and the non-swing scroll and the tooth bottom on the base plate side.
  • a scroll compressor equipped with a so-called compliant mechanism that supports the non-oscillating scroll so as to be movable in the axial direction and presses the non-oscillating scroll toward the swinging scroll side is known. (See, for example, Patent Document 1).
  • the outer diameter of the spacer and the inner diameter of the through hole are different due to a difference in thermal expansion between the spacer and the through hole due to a temperature rise during operation, or due to different materials.
  • the compliant mechanism may malfunction due to the displacement between the spacer and the through hole or the decrease in the clearance between the spacer and the through hole.
  • the compliant mechanism can operate between the spacer and the through hole. Setting the clearance could reduce the relative plane positioning accuracy between the spirals.
  • the present invention is for solving the above-mentioned problems, and a scroll capable of reducing refrigerant leakage loss and improving reliability without causing the compliant mechanism to malfunction even during thermal expansion. It is an object of the present invention to provide a compressor and a refrigeration cycle device.
  • the scroll compressor according to the present invention includes a compression mechanism unit housed in a closed container, a drive mechanism unit that drives the compression mechanism unit, and a drive shaft that transmits the driving force of the drive mechanism unit to the compression mechanism unit.
  • a scroll compressor having a frame fixed in the closed container and a separator for partitioning the inside of the closed container into a high pressure space and a low pressure space, wherein the compression mechanism portion is the low pressure of the separator.
  • a non-oscillating scroll whose plane position is defined so as to be movable in the axial direction of the drive shaft by a guide member fixed between the space side and the frame, and a power supported by the frame and possessed by the drive mechanism unit.
  • the non-swing scroll and the swing scroll each include a swing scroll that is driven by a source via the drive shaft and swings, and each of the non-swing scroll and the swing scroll has spiral teeth that are arranged so as to extend in directions facing each other.
  • a back pressure chamber that extends concentrically with the drive shaft is formed between the back surface of the non-oscillating scroll and the separator, and the non-oscillating scroll and the non-oscillating scroll are separated from each other.
  • a joint for transmitting a moment for rotating the swing scroll in one direction from the swing scroll to the non-swing scroll is arranged, and the non-swing scroll has a guide hole through which the guide member penetrates. The guide hole is formed and has a guide receiving surface that comes into contact with the guide member in the one direction in which the non-oscillating scroll rotates due to the moment transmitted by the joint.
  • the refrigeration cycle apparatus includes a refrigerant circuit having at least a compressor, a condenser, an expansion valve and an evaporator, and uses the scroll compressor as the compressor.
  • the guide receiving surface supports the moment transmitted from the oscillating scroll to the non-oscillating scroll via the joint by coming into contact with the guide member. Therefore, the position and posture of the non-oscillating scroll that is pressed axially toward the oscillating scroll side by the back pressure of the back pressure chamber are automatically determined so as to keep the center of the non-oscillating scroll in a fixed position. As a result, the non-oscillating scroll is pressed in the axial direction in a stable manner without being affected by dimensional changes due to thermal expansion. Therefore, the compliant mechanism does not malfunction even during thermal expansion.
  • the tooth tip gap between the spiral teeth facing each other is kept narrow.
  • FIG. 5 is a plan view for explaining a guide receiving surface in the non-oscillating scroll of FIG.
  • FIG. 1 is a refrigerant circuit diagram showing an example of a refrigeration cycle apparatus 200 using the scroll compressor 1 according to the first embodiment.
  • the refrigerating cycle device 200 performs cooling or heating operation by transferring heat between the outside air and the indoor air via a refrigerant, for example, to perform air conditioning in the room. Functions as a device.
  • the refrigeration cycle device 200 has an indoor unit 201 and an outdoor unit 202.
  • the scroll compressor 1 according to the first embodiment is simply referred to as the compressor 1.
  • the indoor unit 201 and the outdoor unit 202 are connected to each other via the refrigerant pipes 203, 203a, and 203b to form a refrigerant circuit 204 in which the refrigerant circulates.
  • the refrigerant circuit 204 is provided with a compressor 1, a flow path switching device 251, a heat exchanger 252, an expansion valve 253 and an indoor heat exchanger 254, and these are connected via the refrigerant pipes 203, 203a and 203b. ..
  • the outdoor unit 202 has a compressor 1, a flow path switching device 251, a heat exchanger 252, and an expansion valve 253.
  • the compressor 1 compresses and discharges the sucked refrigerant.
  • the flow path switching device 251 is, for example, a four-way valve, which switches the direction of the refrigerant flow path.
  • the refrigerating cycle device 200 can realize a heating operation or a cooling operation by switching the flow of the refrigerant by using the flow path switching device 251 based on the instruction from the control unit 205.
  • the heat exchanger 252 exchanges heat between the refrigerant and the outdoor air. Further, the heat exchanger 252 is provided with an outdoor blower 255 in order to improve the efficiency of heat exchange between the refrigerant and the outdoor air.
  • the heat exchanger 252 functions as an evaporator during the heating operation and exchanges heat between the low-pressure refrigerant flowing in from the refrigerant pipe 203b side and the outdoor air to evaporate and vaporize the refrigerant. , Flow out to the refrigerant pipe 203a side. Further, the heat exchanger 252 functions as a condenser during the cooling operation, and is between the refrigerant compressed by the compressor 1 flowing from the refrigerant pipe 203a side via the flow path switching device 251 and the outdoor air. The refrigerant is condensed and liquefied, and is discharged to the refrigerant pipe 203b side.
  • the external fluid is not limited to the gas containing the outdoor air, and may be a liquid containing water.
  • the expansion valve 253 is a throttle device that controls the flow rate of the refrigerant, and adjusts the pressure of the refrigerant by adjusting the flow rate of the refrigerant flowing through the refrigerant pipe 203 by changing the opening degree of the expansion valve 253. During the cooling operation, the expansion valve 253 expands the high-pressure liquid state refrigerant into the low-pressure gas-liquid two-phase state refrigerant to reduce the pressure.
  • the expansion valve 253 is not limited to this, and an electronic expansion valve, a capillary tube, or the like may be used as long as the same effect can be obtained. For example, when the expansion valve 253 is composed of an electronic expansion valve, the opening degree is adjusted based on the instruction of the control unit 205.
  • the indoor unit 201 includes an indoor heat exchanger 254 that exchanges heat between the refrigerant and the indoor air, and an indoor blower 257 that adjusts the flow of air that the indoor heat exchanger 254 exchanges heat with.
  • the indoor heat exchanger 254 acts as a condenser during the heating operation, exchanges heat between the refrigerant flowing in from the refrigerant pipe 203a side and the indoor air, condenses the refrigerant and liquefies it, and causes the refrigerant pipe. Let it flow out to the 203b side. Further, the indoor heat exchanger 254 functions as an evaporator during the cooling operation. The indoor heat exchanger 254 exchanges heat between the refrigerant that has been brought into a low pressure state by the expansion valve 253 that has flowed in from the refrigerant pipe 203b side and the indoor air, and causes the refrigerant to take away the heat of the air and evaporate it.
  • the external fluid is not limited to the gas containing the indoor air, and may be a liquid containing water.
  • the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 1 flows into the heat exchanger 252 via the flow path switching device 251.
  • the gas refrigerant that has flowed into the heat exchanger 252 is condensed by heat exchange with the outside air blown by the outdoor blower 255, becomes a low-temperature refrigerant, and flows out from the heat exchanger 252.
  • the refrigerant flowing out of the heat exchanger 252 is expanded and depressurized by the expansion valve 253 to become a low-temperature low-pressure gas-liquid two-phase refrigerant.
  • This gas-liquid two-phase refrigerant flows into the indoor heat exchanger 254 of the indoor unit 201, evaporates by heat exchange with the indoor air blown by the indoor blower 257, becomes a low-temperature low-pressure gas refrigerant, and becomes an indoor heat exchanger. Outflow from 254. At this time, the indoor air that has been cooled by being absorbed by the refrigerant becomes air-conditioned air (blown air) and is blown out from the indoor unit 201 into the room that is the air-conditioned space. The gas refrigerant flowing out of the indoor heat exchanger 254 is sucked into the compressor 1 via the flow path switching device 251 and is compressed again. In the cooling operation of the refrigeration cycle device 200, the above operation is repeated (indicated by a solid arrow in FIG. 1).
  • the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 1 flows into the indoor heat exchanger 254 of the indoor unit 201 via the flow path switching device 251.
  • the gas refrigerant flowing into the indoor heat exchanger 254 condenses by heat exchange with the indoor air blown by the indoor blower 257, becomes a low-temperature refrigerant, and flows out from the indoor heat exchanger 254.
  • the indoor air that has been warmed by receiving heat from the gas refrigerant becomes conditioned air (blown air) and is blown out into the room from the indoor unit 201.
  • the refrigerant flowing out of the indoor heat exchanger 254 is expanded and depressurized by the expansion valve 253 to become a low-temperature low-pressure gas-liquid two-phase refrigerant.
  • This gas-liquid two-phase refrigerant flows into the heat exchanger 252 of the outdoor unit 202, evaporates by heat exchange with the outside air blown by the outdoor blower 255, becomes a low-temperature low-pressure gas refrigerant, and flows out from the heat exchanger 252. To do.
  • the gas refrigerant flowing out of the heat exchanger 252 is sucked into the compressor 1 via the flow path switching device 251 and is compressed again. In the heating operation of the refrigeration cycle device 200, the above operation is repeated (indicated by the broken line arrow in FIG. 1).
  • FIG. 2 is a schematic explanatory view showing a vertical cross section of the scroll compressor 1 according to the first embodiment.
  • FIG. 3 is an enlarged explanatory view showing a compression mechanism unit 10 in the scroll compressor 1 of FIG.
  • FIG. 4 is a plan view showing the non-oscillating scroll 11 in the compression mechanism unit 10 of FIG.
  • FIG. 5 is a plan view for explaining the compression mechanism unit 10 of FIG.
  • FIG. 6 is a plan view for explaining the compression mechanism unit 10 of FIG.
  • FIG. 7 is a perspective view showing the joint 13 in the compression mechanism portion 10 of FIG.
  • FIG. 8 is a plan view for explaining the guide receiving surface 116 in the non-oscillating scroll 11 of FIG.
  • the scroll compressor 1 transmits the driving force of the shell 2, the compression mechanism unit 10, the drive mechanism unit 20 for driving the compression mechanism unit 10, and the drive mechanism unit 20 to the compression mechanism unit 10.
  • the drive shaft 3 is provided, and the main frame 4 fixed in the shell 2 is provided.
  • the compression mechanism unit 10, the drive mechanism unit 20, the drive shaft 3, and the main frame 4 are housed in a shell 2 as a closed container forming a tubular housing in which both upper and lower ends in the vertical direction are closed.
  • the shell 2 is made of a conductive member such as metal.
  • a subframe 5 is provided in the lower part of the shell 2.
  • the scroll compressor 1 is a so-called vertical scroll compressor in which the central axis of the drive shaft 3 having the rotating shaft and the driving shaft is used in a state of being substantially perpendicular to the ground.
  • the suction pipe 6 is connected to the shell 2 by welding or the like.
  • the suction pipe 6 is a pipe that introduces the refrigerant into the shell 2 and communicates with the inside of the shell 2.
  • a discharge pipe 7 is connected to the upper part of the shell 2 by welding or the like.
  • the discharge pipe 7 is a pipe that discharges the refrigerant to the outside of the shell 2 and communicates with a high-pressure space 21 formed in the upper part of the shell 2 as a discharge space described later.
  • the drive shaft 3 is a long metal rod-shaped member, which is provided in the shell 2 and transmits the driving force of the drive mechanism unit 20 to the compression mechanism unit 10.
  • the drive shaft 3 includes a spindle portion 31, an eccentric shaft portion 32, and an oil passage 33.
  • the spindle portion 31 is a shaft that constitutes the main portion of the drive shaft 3.
  • the central axis of the spindle portion 31 is arranged so as to coincide with the central axis of the shell 2.
  • a rotor 220 of a drive mechanism unit 20, which will be described later, is contact-fixed to the outer surface of the spindle portion 31.
  • the eccentric shaft portion 32 is provided on the upper side of the spindle portion 31.
  • the central axis of the eccentric shaft portion 32 is eccentric with respect to the central axis of the main shaft portion 31.
  • the eccentric shaft portion 32 is inserted into the tubular portion 123 of the swing scroll 12, which will be described later, via the slider 9.
  • the oil passage 33 is provided so as to penetrate vertically inside the main shaft portion 31 and the eccentric shaft portion 32.
  • the upper side of the spindle portion 31 of the drive shaft 3 is inserted into the spindle portion 43 of the main frame 4, which will be described later. Further, the lower side of the spindle portion 31 of the drive shaft 3 is inserted and fixed to the sub-bearing portion 51 of the subframe 5, which will be described later. As a result, the eccentric shaft portion 32 is arranged in the cylinder of the tubular portion 123. Further, the rotor 220 that is contact-fixed to the spindle portion 31 is arranged so that the outer peripheral surface thereof and the inner peripheral surface of the stator 210, which will be described later, are maintained with a predetermined gap.
  • a first balancer 34 is provided in the middle of the upper side of the spindle portion 31.
  • a second balancer 2201 is provided below the rotor 220 located below the spindle 31. The first balancer 34 and the second balancer 2201 are provided to cancel the unbalanced state due to the swinging motion of the swinging scroll 12 in the compression mechanism unit 10 described later.
  • the main frame 4 is a hollow metal frame having a cavity formed in the center, and is provided inside the shell 2.
  • the outer peripheral end portion 41 as a fixing portion is fixed to the inner wall surface of the shell 2.
  • a storage space 42 is formed along the longitudinal direction of the shell 2 extending coaxially with the central axis of the drive shaft 3.
  • the accommodation space 42 has a main bearing portion 43 as a bearing portion formed in a stepped shape in which the upper side is open and the internal space is narrowed toward the lower side.
  • the main bearing portion 43 rotatably supports the drive shaft 3.
  • the main bearing portion 43 is continuously formed on the lower side of the main frame 4.
  • a shaft hole 431 is formed inside the main bearing portion 43.
  • the shaft hole 431 penetrates the main bearing portion 43 in the vertical direction, that is, the main bearing portion 43 on the upper side and the lower side, and the upper side thereof communicates with the accommodation space 42.
  • a suction port 44 is formed on the outer peripheral side of the main frame 4.
  • the suction port 44 is a space that penetrates the main frame 4 in the vertical direction, that is, the main frame 4 on the upper side and the lower side.
  • the number of suction ports 44 is not limited to one, and a plurality of suction ports 44 may be formed.
  • a subframe 5 is provided at the bottom of the shell 2. As shown in FIG. 2, the subframe 5 is a metal frame, and is provided inside the shell 2 on the lower side of the drive mechanism unit 20. The subframe 5 is fixedly supported on the lower inner wall surface of the shell 2 by shrink fitting, welding, or the like.
  • the subframe 5 includes an auxiliary bearing portion 51 and an oil pump 52.
  • the sub-bearing portion 51 is a ball bearing provided on the upper side of the central portion of the sub-frame 5.
  • a hole is formed in the center of the auxiliary bearing portion 51 so as to penetrate the auxiliary bearing portion 51 in the vertical direction, that is, on the upper side and the lower side.
  • the oil pump 52 is provided on the lower side of the central portion of the subframe 5.
  • the oil pump 52 is arranged by immersing at least a part of the lubricating oil stored in the oil reservoir 8 provided in the lower part of the shell 2.
  • the lubricating oil stored in the oil reservoir 8 is sucked up by the oil pump 52, passes through the oil passage 33 in the drive shaft 3, reduces wear between mechanically contacting parts such as the compression mechanism portion 10, and slides. Adjust the temperature of the moving part or improve the sealing performance.
  • lubricating oil for example, in addition to refrigerating machine oil containing an ester-based synthetic oil, an oil having excellent lubrication characteristics, electrical insulation, stability, refrigerant solubility, low-temperature fluidity, etc., and having an appropriate viscosity. Is preferable to use.
  • a separator 101 is provided in the upper part of the shell 2.
  • the separator 101 partitions the internal space of the shell 2 as a high-pressure space 21 that communicates the space above the separator 101 with the discharge pipe 7 and a low-pressure space 22 that communicates with the discharge pipe 7.
  • the drive mechanism unit 20, the subframe 5, the oil reservoir 8, and the like are arranged below, and the compression mechanism unit 10 and the main frame 4 are arranged above. Etc. are arranged.
  • the compression mechanism unit 10 is arranged between the separator 101 and the main frame 4, and includes a non-oscillating scroll 11 and an oscillating scroll 12.
  • the compression mechanism unit 10 is a scroll compression mechanism that compresses the refrigerant.
  • the non-oscillating scroll 11 is made of a metal such as cast iron, and includes a first circular base plate 111 and a first spiral tooth 112.
  • the first circular base plate 111 is formed in a disk shape, and a discharge port 113 is formed in the center thereof in the vertical direction, that is, through the first circular base plate 111 on the upper side and the lower side.
  • the first spiral tooth 112 protrudes from the lower surface of the first circular base plate 111 to form a spiral wall portion, the tip of which protrudes toward the swing scroll 12 located on the lower side. ..
  • the non-oscillating scroll 11 is formed by integrally molding the first circular base plate 111 and the first spiral teeth 112.
  • a high-pressure discharge chamber 1011 and an intermediate pressure back pressure chamber 1012 are formed in an annular shape between the non-oscillating scroll 11 and the separator 101, respectively.
  • the discharge chamber 1011 and the back pressure chamber 1012 are concentrically partitioned by the sealing members 26 and 27.
  • a discharge port 113 of the non-oscillating scroll 11 is opened on the low pressure space 22 side of the discharge chamber 1011 so that the discharge chamber 1011 and the intermediate pressure compression chamber 28 described later are connected to each other. It communicates through the discharge port 113.
  • a discharge port 1013 of the separator 101 is opened on the high pressure space 21 side of the discharge chamber 1011 so that the discharge chamber 1011 and the high pressure space 21 communicate with each other via the discharge port 1013.
  • a discharge valve 23 and a discharge valve stopper 231 are provided at the opening on the high pressure space 21 side of the separator 101 in the discharge port 1013 in order to prevent backflow.
  • the compression chamber 28 and the back pressure chamber 1012 are communicated with each other.
  • An bleed port 114 for introducing an intermediate pressure is formed in the back pressure chamber 1012.
  • the bleed port 114 is opened at a position symmetrical to the inward surface side and the outward surface side of the first spiral tooth 112. In the case of the first embodiment, the bleeding ports 114 are provided at two places.
  • an bleed air port 114 formed at a portion located between the back pressure chamber 1012 and the compression chamber 28 in the first circular base plate 111 is opened.
  • the back pressure chamber 1012 and the compression chamber 28 communicate with each other via the bleed air port 114.
  • a relief port 1014 penetrating the upper side and the lower side of the separator 101 is opened on the high pressure space 21 side of the back pressure chamber 1012.
  • the back pressure chamber 1012 and the high pressure space 21 communicate with each other via the bleed air port 114.
  • a relief valve 24 and a relief valve stopper 241 are provided at the opening on the high pressure space 21 side of the separator 101 in the relief port 1014 in order to prevent backflow.
  • an elongated guide hole 115 through which a columnar guide member 25 fixed to the separator 101 and the swing scroll 12 penetrates.
  • the guide hole 115 has an elongated hole shape extending in the radial direction, and the non-oscillating scroll 11 rotates on the inner peripheral surface thereof due to the moment transmitted by the joint 13 described later.
  • a guide receiving surface 116 that comes into contact with the guide member 25 in one direction is formed.
  • the guide receiving surface 116 is arranged so as to extend in the outer peripheral direction of the non-oscillating scroll 11, and a contact point with the guide member 25 is formed so as to be movable in the outer peripheral direction relative to the guide member 25.
  • the guide member 25 is formed of a convex surface
  • the guide receiving surface 116 is formed of a flat surface or a concave surface.
  • the radius of curvature of the flat surface or the concave surface of the guide receiving surface 116 is formed to be larger than the radius of curvature of the convex surface of the guide member 25.
  • the positional relationship of the guide holes 115 on the outer circumference of the non-oscillating scroll 11 will be described with reference to FIG.
  • the distance between the guide receiving surfaces 116 located opposite to each other is D.
  • the distance D between the guide receiving surfaces 116 located opposite to each other will be described.
  • the center line connecting the centers of the guide holes 115 located diagonally to the non-oscillating scroll 11 is used as a reference. ..
  • each guide receiving surface 116 is a flat surface portion oriented in the circumferential direction, and they are arranged at a distance D / 2 from the center line connecting the centers of the guide holes 115 located diagonally to each other. ..
  • the swing scroll 11 is arranged between the swing scroll 11 and the swing scroll 12, and contributes to the transmission of the moment of the swing scroll 12 described later to the non-rock scroll 11.
  • a circular first joint hole 117 is formed in which the joint 13 to be used is arranged.
  • the first joint holes 117 are formed at three places, for example, at equal intervals along the outer circumference of the first circular base plate 111.
  • the swing scroll 12 is made of a metal such as aluminum, and includes a second circular base plate 121, a second spiral tooth 122, and a tubular portion 123. There is.
  • the second circular base plate 121 is formed in a disk shape.
  • the second spiral tooth 122 protrudes from the upper surface of the second circular base plate 121 to form a spiral wall portion, and the tip thereof protrudes toward the non-oscillating scroll 11 located on the upper side.
  • the upper surface on which the second spiral tooth 122 is formed is the tooth bottom surface.
  • the swing scroll 12 is formed by integrally molding the second circular base plate 121 and the second spiral tooth 122.
  • the tubular portion 123 is a cylindrical boss formed so as to project downward from the center of the lower surface of the second circular base plate 121.
  • a swing bearing that rotatably supports an eccentric shaft portion 32 inserted via a slider 9 described later, a so-called journal bearing, has a central axis of a drive shaft 3 and a central axis of the drive shaft 3. It is provided so as to be parallel.
  • a circular shape is provided on the outer peripheral side of the second circular base plate 121 of the rocking scroll 12 to provide a joint 13 to be described later, which is arranged between the non-rocking scroll 11 and the rocking scroll 12.
  • the second joint hole 124 is formed.
  • the second joint holes 124 are formed at three places, for example, at equal intervals along the outer circumference of the second circular base plate 121.
  • a columnar guide member 25 fixed to the separator 101 and the swing scroll 12 is provided on the outer peripheral side of the second circular base plate 121.
  • a curved notch-shaped recess 125 is formed to avoid contact.
  • the recessed portions 125 are formed at four locations, for example, at equal intervals along the outer circumference of the second circular base plate 121, corresponding to the arrangement positions of the guide members 25.
  • an intermediate pressure compression chamber 28 is formed by engaging the first spiral tooth 112 of the non-oscillating scroll 11 and the second spiral tooth 122 of the rocking scroll 12 with each other. Tooth.
  • the volume of the compression chamber 28 decreases from the outside to the inside in the radial direction. Therefore, the refrigerant is taken in from the outer end side of the first spiral tooth 112 and the second spiral tooth 122, and is gradually compressed by being moved to the central side.
  • the compression chamber 28 communicates with the discharge port 113 at the central portion of the non-oscillating scroll 11.
  • the refrigerant compressed in the compression chamber 28 passes through the discharge port 113, the discharge chamber 1011 and the discharge port 1013, opens the discharge valve 23 at that pressure, and is discharged into the high-pressure space 21 as the discharge space in the shell 2. .. After that, the discharged refrigerant flows out from the discharge pipe 7.
  • a joint 13 is arranged between the non-oscillating scroll 11 and the oscillating scroll 12.
  • the joint 13 has a first cylindrical member 131 which is a first cylindrical member and a second cylindrical member 132 which is a second cylindrical member having a diameter smaller than that of the first cylindrical member 131.
  • the first cylindrical member 131 and the second cylindrical member 132 form a crank pin type that is eccentrically overlapped.
  • a plurality of joints 13 are provided in the circumferential direction on the outer peripheral side of the non-swing scroll 11 and the swing scroll 12 (three in the case of the first embodiment).
  • the joint 13 is oriented in one direction from the swing scroll 12 to the non-swing scroll 11, that is, in the clockwise direction M. It transmits the moment to rotate.
  • the guide member 25, the guide receiving surface 116, and the joint 13 described above are from the outward surface winding end position of the first spiral tooth 112 of the non-oscillating scroll 11 to the maximum 270 deg position. It is preferably arranged in a range.
  • FIG. 6 shows a state in which the second spiral tooth 122 of the swing scroll 12, the joint 13, and the guide member 25 are superposed on the non-rock scroll 11.
  • FIG. 7 shows a state in which the second circular base plate 121 of the oscillating scroll 12 is superposed on the non-oscillating scroll 11 when viewed from the tubular portion 123 side.
  • each guide hole 115 is formed at positions of 90 deg each on the outer peripheral side of the first circular base plate 111.
  • Corresponding guide members 25 are arranged through the guide holes 115.
  • the first joint holes 117 are formed at three positions on the outer peripheral side of the first circular base plate 111 at every 120 deg.
  • the first cylindrical member 131 of the joint 13 is fitted into the first joint hole 117.
  • the second joint holes 124 are formed at three positions on the outer peripheral side of the second circular base plate 121 at every 120 deg.
  • the second cylindrical member 132 of the joint 13 is fitted into the second joint hole 124.
  • the second cylindrical member 132 of the joint 13 is fitted into the second joint hole 124 formed at the corresponding position of the second circular base plate 121 of the swing scroll 12, so that the joint 13 can be moved from the swing scroll 12. A moment can be transmitted to the non-oscillating scroll 11 via the swing scroll 11.
  • the non-oscillating scroll 11 is driven by the guide member 25 fixed between the low pressure space 22 side of the separator 101 and the main frame 4 without causing the compliant mechanism to malfunction even during thermal expansion.
  • the plane position is defined so as to be movable in the axial direction of the shaft 3. Further, between the non-oscillating scroll 11 and the oscillating scroll 12, the tooth tip gap between the first spiral tooth 112 and the second spiral tooth 122 facing each other is kept narrow.
  • the drive mechanism unit 20 is provided below the main frame 4 in the shell 2.
  • the drive mechanism unit 20 includes a stator 210 and a rotor 220.
  • the stator 210 is an annular stator.
  • the stator 210 is formed, for example, by arranging a plurality of teeth in which windings are wound through an insulating layer in an annular shape on an iron core in which a plurality of electromagnetic steel plates are laminated.
  • the stator 210 is fixedly supported in the shell 2 by shrink fitting or the like.
  • the rotor 220 is arranged in the internal space of the stator 210.
  • the rotor 220 is a cylindrical rotor arranged in a central hole formed inside the stator 210, which is an annular stator.
  • the rotor 220 has a permanent magnet built in an iron core in which a plurality of electromagnetic steel sheets and the like are laminated.
  • a hole is formed in the center of the rotor 220 in the vertical direction, that is, through the rotor 220 on the upper side and the lower side.
  • the slider 9 is a connecting member that connects the swing scroll 12 and the drive shaft 3.
  • the slider 9 is made of a metal such as iron.
  • the slider 9 is a tubular member. The slider 9 is fitted into each of the eccentric shaft portion 32 and the tubular portion 123.
  • FIG. 9 is an explanatory diagram provided for explaining the positioning of the non-oscillating scroll 11 of FIG.
  • FIG. 10 is an explanatory diagram provided for explaining the positioning of the non-oscillating scroll 11 of FIG.
  • FIG. 11 is an explanatory diagram provided for explaining the positioning of the non-oscillating scroll 11 of FIG.
  • FIG. 12 is an explanatory diagram provided for explaining the operation of the compression mechanism unit 10 of FIG.
  • the moment transmitted to the non-oscillating scroll 11 is supported by the guide member 25 when the inner peripheral surface of the guide hole 115 of the non-oscillating scroll 11 corresponding to each of the guide members 25 comes into contact with the non-oscillating scroll 11.
  • the center of the moving scroll 11 is kept at one point. The situation in which the non-oscillating scroll 11 is positioned due to the relationship between the guide receiving surface 116 and the guide member 25 will be described later.
  • the imbalance caused by the movement of the swing scroll 12 is balanced by the first balancer 34 attached to the drive shaft 3 and the second balancer 2201 attached to the rotor 220.
  • the lubricating oil stored in the oil reservoir 8 at the lower part of the shell 2 is supplied to each sliding portion through the oil passage 33 provided in the drive shaft 3.
  • the gas sucked into the shell 2 from the suction pipe 6 is taken into the compression chamber 28 between the non-rocking scroll 11 and the rocking scroll 12 and compressed.
  • the compressed gas is discharged from the discharge valve 23 to the high-pressure space 21 via the discharge port 113 of the non-oscillating scroll 11, the discharge chamber 1011 and the discharge port 1013 of the separator 101, and is discharged from the discharge pipe 7 to the outside of the shell 2. Is discharged to.
  • the non-oscillating scroll 11 receives the pressure of the discharge chamber 1011 and the back pressure chamber 1012, and the plane position and the posture are regulated by a plurality of guide members 25 arranged on the outer circumference, while resisting the pressure in the compression chamber 28. It is pressed in the axial direction toward the swing scroll 12. As a result, the gap between the tooth tips of the first spiral tooth 112 of the non-oscillating scroll 11 and the second spiral tooth 122 of the rocking scroll 12 is minimized, and the leakage loss is reduced.
  • the non-oscillating scroll 11 is pressed axially toward the oscillating scroll 12 against the pressure in the compression chamber 28 as described above without being fixed by bolt tightening or the like, so that the so-called compliant mechanism Consists of.
  • the scroll compressor 1 when the scroll compressor 1 is operated under a low compression ratio condition, the back pressure is reached when the inside of the compression chamber 28 reaches the discharge pressure before the discharge port 113 opens in the compression chamber 28 due to the spiral built-in volume ratio.
  • the overcompression loss is reduced by discharging from the chamber 1012 through the relief port 1014 and the relief valve 24 to the high pressure space 21.
  • the positional relationship between the center of the non-oscillating scroll 11 determined by the arrangement of the guide holes 115 and the center of the main frame 4 or the separator 101 determined by the arrangement of the guide members 25 is uniquely determined. Since the non-oscillating scroll 11 is only positioned by the contact between the guide receiving surface 116 and the guide member 25, it can move along the guide member 25 in the axial direction, which hinders the function of the compliant mechanism. do not. Further, the guide receiving surface 116 can be positioned as much as possible without impairing the compliant function even if the relative position (distance from the center of the guide hole 115) between the guide receiving surface 116 and the guide member 25 changes due to thermal expansion or the like. The radial width of the flat surface portion as the receiving surface 116 is set.
  • the posture of the non-oscillating scroll 11, that is, the angle with respect to the horizontal is equal to the size of the distance D between the guide receiving surfaces 116 located opposite to each other and the size of the diameter d of the guide member 25.
  • the relative rotation of the non-oscillating scroll 11 and the oscillating scroll 12 in the case of d is "0". Then, when the relationship between D and d changes due to thermal expansion, dimensional tolerance, or the like, the posture of the non-oscillating scroll 11 changes as shown in FIGS. 11 and 13.
  • FIG. 10 shows the case where d> D.
  • the timing at which the surface 116 comes into contact with the guide member 25 is delayed, and the surface 116 is positioned by rotating relative to each other by ⁇ in the clockwise direction M.
  • the attitude change amount ⁇ in FIGS. 10 and 11 is the separator 101 to the guide member 25 and the guide member 25 of a series of parts group consisting of the rotor 220, the drive shaft 3, the swing scroll 12, the joint 13, and the non-swing scroll 11.
  • This is the angle with respect to the stationary system called the main frame 4. Therefore, there is no particular problem as long as it is a minute amount caused by thermal expansion or dimensional variation and does not always fluctuate during operation.
  • non-oscillating scrolls also called fixed frames
  • the variation is "0". , Which is equivalent to having a certain tolerance.
  • FIG. 12 shows 90 deg of the operating positional relationship between the non-swing scroll 11, the joint 13, the second spiral tooth 122 of the swing scroll 12, the second circular base plate 121, and the guide member 25 during one rotation. It shows the state of rotation every time.
  • the swing scroll 12 turns while avoiding interference with the guide member 25 by the recessed portion 125 formed on the outer periphery of the second circular base plate 121. Then, the moment is transmitted to the non-oscillating scroll 11 via the joint 13.
  • the relative positions and postures of the non-swinging scroll 11 and the swinging scroll 12 are determined.
  • the compression chamber 28 formed between the first spiral tooth 112 and the second spiral tooth 122 of the non-rock scroll 11 and the swing scroll 12 reduces the volume, and the gas is released. You can see how it is compressed.
  • the guide receiving surface 116 comes into contact with the guide member 25 from the swing scroll 12 via the joint 13. Supports the moment transmitted to the non-oscillating scroll 11. Therefore, the position and posture of the non-oscillating scroll 11 pressed axially toward the oscillating scroll 12 by the back pressure of the back pressure chamber 1012 are automatically determined so as to keep the center of the non-oscillating scroll 11 in place. .. As a result, the non-oscillating scroll 11 is pressed in the axial direction in a stable manner without being affected by dimensional changes due to thermal expansion. Therefore, the compliant mechanism does not malfunction even during thermal expansion.
  • the tooth tip gap between the first spiral tooth 112 and the second spiral tooth 122 facing each other is kept narrow.
  • FIG. 13 is a perspective view showing a joint 13 in the scroll compressor 1 according to the second embodiment.
  • FIG. 14 is an explanatory diagram for explaining the operation of the compression mechanism unit 10 of the scroll compressor 1 according to the second embodiment.
  • crank pin type joint 13 in which the second cylindrical member 132 is eccentrically overlapped on the first cylindrical member 131 is arranged at three locations on the outer periphery of the non-oscillating scroll 11 and the oscillating scroll 12, and is guided.
  • the case where the member 25 and the guide hole 115 are similarly arranged at four locations on the outer periphery has been described.
  • this portion is another aspect, and the other configurations are the same as those in the first embodiment.
  • the joint 13 is a first key member 133 and a second key member, which are first key members made of a rectangular parallelepiped, respectively.
  • the shape may be formed by stacking the two key members 134 in a state of being orthogonal to each other.
  • the joints 13 are arranged at a plurality of locations (for example, two locations) on the outer periphery of the non-oscillating scroll 11 and the swinging scroll 12. You may do so. Even if the guide member 25 and the guide hole 115 are also arranged at three locations on the outer periphery of the non-oscillating scroll 11 and the oscillating scroll 12, the functions are the same as those of the first embodiment.
  • the first joint hole 117 in the first circular base plate 111 of the non-oscillating scroll 11 is formed in an elongated hole shape that slidably holds the first key member 133.
  • the second joint hole 124 in the second circular base plate 121 of the swing scroll 12 is formed in an elongated hole shape for slidably holding the second key member 134.
  • the first joint hole 117 and the second joint hole 124 are arranged at two locations on the outer periphery of the non-swing scroll 11 and the swing scroll 12.
  • the position at the end of the outward surface winding of the first spiral tooth 112 of 11 (the position in the 12 o'clock direction in FIG. 4 or FIG. 12 or FIG. 14) is used as a reference.
  • the first guide member 25 and the guide hole 115 are arranged at the reference position, and the nth guide member 25 and the guide hole 115 are arranged in the range from the reference position to the position of 180 to 270 deg.
  • n-2 guide members 25 and guide holes 115 are arranged so as to divide the angle range from the first to the nth into n-1. Further, the joint 13 is also distributed and arranged within the range from the first guide member 25 and the guide hole 115 to the nth guide member 25 and the guide hole 115 so as not to interfere with the guide member 25 and the guide hole 115. Is preferable.
  • 1 scroll compressor 2 shell, 21 high pressure space, 22 low pressure space, 23 discharge valve, 231 discharge valve stopper, 24 relief valve, 241 relief valve stopper, 25 guide member, 26 seal member, 28 compression chamber, 3 drive shaft, 31 spindle, 32 eccentric shaft, 33 oil passage, 34 first balancer, 4 main frame, 41 outer peripheral end, 42 accommodation space, 43 main bearing, 431 shaft hole, 44 suction port, 5 subframe, 51 Auxiliary bearing, 52 oil pump, 6 suction pipe, 7 discharge pipe, 8 oil reservoir, 9 slider, 10 compression mechanism, 101 separator, 1011 discharge chamber, 1012 back pressure chamber, 1013 discharge port, 1014 relief port, 11 non- Swing scroll, 111 1st circular base plate, 112 1st spiral tooth, 113 discharge port, 114 air extraction port, 115 guide hole, 116 guide receiving surface, 117 1st joint hole, 12 rocking scroll, 121 2nd circular base Plate, 122 second spiral tooth, 123 tubular part, 124 second joint hole, 125 recessed part, 13 joint,

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2019/045428 2019-11-20 2019-11-20 スクロール圧縮機および冷凍サイクル装置 WO2021100141A1 (ja)

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JP2021558092A JPWO2021100141A1 (enrdf_load_stackoverflow) 2019-11-20 2019-11-20
PCT/JP2019/045428 WO2021100141A1 (ja) 2019-11-20 2019-11-20 スクロール圧縮機および冷凍サイクル装置

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH023090U (enrdf_load_stackoverflow) * 1988-06-20 1990-01-10
JPH06264877A (ja) * 1993-03-15 1994-09-20 Toshiba Corp スクロ−ル形圧縮機
JPH11287190A (ja) * 1998-04-01 1999-10-19 Toyota Autom Loom Works Ltd スクロール型流体機械
JP2003013871A (ja) * 2001-04-25 2003-01-15 Matsushita Seiko Co Ltd 自転阻止装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH023090U (enrdf_load_stackoverflow) * 1988-06-20 1990-01-10
JPH06264877A (ja) * 1993-03-15 1994-09-20 Toshiba Corp スクロ−ル形圧縮機
JPH11287190A (ja) * 1998-04-01 1999-10-19 Toyota Autom Loom Works Ltd スクロール型流体機械
JP2003013871A (ja) * 2001-04-25 2003-01-15 Matsushita Seiko Co Ltd 自転阻止装置

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