WO2022070382A1 - スクロール圧縮機、及び、冷凍サイクル装置 - Google Patents

スクロール圧縮機、及び、冷凍サイクル装置 Download PDF

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Publication number
WO2022070382A1
WO2022070382A1 PCT/JP2020/037421 JP2020037421W WO2022070382A1 WO 2022070382 A1 WO2022070382 A1 WO 2022070382A1 JP 2020037421 W JP2020037421 W JP 2020037421W WO 2022070382 A1 WO2022070382 A1 WO 2022070382A1
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WO
WIPO (PCT)
Prior art keywords
valve
valve seat
scroll compressor
discharge
opening
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/JP2020/037421
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
雄太郎 岩本
浩平 達脇
友寿 松井
浩二 増本
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 JP2022553374A priority Critical patent/JP7337283B2/ja
Priority to US18/006,194 priority patent/US12006934B2/en
Priority to PCT/JP2020/037421 priority patent/WO2022070382A1/ja
Publication of WO2022070382A1 publication Critical patent/WO2022070382A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • F04B39/1086—Adaptations or arrangements of distribution members the members being reed valves flat annular reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C18/0207—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 both members having co-operating elements in spiral form
    • F04C18/0215—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 both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/102—Geometry of the inlet or outlet of the outlet

Definitions

  • the present disclosure relates to a scroll compressor and a refrigeration cycle device provided with the compressor, and particularly to the structure of a discharge port of a compression mechanism unit.
  • the scroll compressor is provided with a discharge chamber in which the refrigerant compressed by the compression mechanism unit is housed, and the compression mechanism unit has a compression chamber for discharging the refrigerant compressed in the compression chamber to the discharge chamber.
  • a discharge port is formed to communicate with the discharge chamber.
  • a discharge valve mechanism for opening and closing the discharge port is provided on the discharge chamber side of the fixed scroll, which is a component of the compression mechanism (see, for example, Patent Document 1).
  • This discharge valve mechanism has a function of partitioning a high-pressure space on the discharge chamber side and a low-pressure space on the compression mechanism portion side using a fixed scroll before compressing the refrigerant.
  • the discharge valve mechanism of the conventional scroll compressor is provided with a plate-shaped valve that opens and closes the discharge port, and a valve seat that is provided around the discharge port and on which the valve is seated.
  • the valve is seated only on the valve seat, but the part covering the discharge port of the valve is not seated anywhere and cannot be supported, so the load when opening and closing the discharge port deforms and bends into the discharge port. I'm sorry.
  • the load applied to the valve increases and the amount of deflection of the portion covering the discharge port of the valve also increases, so that the reliability of the valve decreases.
  • the present disclosure is for solving the above-mentioned problems, and provides a scroll compressor in which the amount of valve deflection is suppressed, and a refrigeration cycle device.
  • the scroll compressor according to the present disclosure is a compression mechanism unit that forms a shell forming an outer shell of a closed container and a compression chamber that is housed in the shell and compresses a refrigerant, and is surrounded by the shell and the compression mechanism unit.
  • a compression mechanism unit having a discharge port formed as a through hole for communicating the discharge chamber and the compression chamber, which is a space, and a discharge valve mechanism provided in the compression mechanism unit on the side facing the discharge chamber to open and close the discharge port.
  • the discharge valve mechanism is formed in a plate shape with a valve seat provided at the outlet of the discharge port, which is the opening end on the outlet side of the refrigerant, and closes the valve seat when seated on the valve seat.
  • valve seat is provided on the inner peripheral side of the annular portion and the annular portion formed so as to form the edge of the opening of the outlet portion, and partitions the opening of the outlet portion, and is a through hole. It has a valve support portion constituting a plurality of valve seat holes, and the valve comes into contact with at least a part of the valve support portion and the annular portion when seated on the valve seat.
  • the refrigeration cycle device is provided with the scroll compressor.
  • the valve seat of the scroll compressor is provided on the annular portion formed so as to form the edge of the opening of the outlet portion and on the inner peripheral side of the annular portion. It has a valve support portion that partitions the opening of the outlet portion and constitutes a plurality of valve seat holes. Then, when the valve is seated on the valve seat, the valve comes into contact with at least a part of the valve support portion provided in the discharge port and the annular portion.
  • valve Since the valve abuts on the valve seat not only at the position facing the edge of the outlet portion but also at a plurality of positions, the amount of deflection of the valve can be dispersed and the amount of deflection due to the load when the valve is seated can be suppressed.
  • FIG. 3 is a top view conceptually showing an enlarged valve seat portion of the scroll compressor according to the first embodiment. It is an enlarged view near the outlet part of the discharge valve mechanism shown in FIG. It is an enlarged view which conceptually shows the 1st modification of the valve support part which concerns on Embodiment 1. FIG. It is an enlarged view which conceptually shows the 2nd modification of the valve support part which concerns on Embodiment 1.
  • FIG. It is a top view which shows the valve seat of the scroll compressor which concerns on Embodiment 2.
  • FIG. It is a top view which shows the valve seat of the scroll compressor which concerns on Embodiment 3.
  • FIG. It is a top view which shows the valve seat of the scroll compressor which concerns on Embodiment 4.
  • FIG. It is a top view which shows the valve seat of the scroll compressor which concerns on Embodiment 5.
  • FIG. 3 is a top view conceptually showing an enlarged valve seat portion of the scroll compressor according to the eighth embodiment. It is a schematic sectional drawing which shows the discharge valve mechanism of the scroll compressor which concerns on a comparative example. It is a schematic schematic diagram which shows the refrigerating cycle apparatus provided with the scroll compressor which concerns on embodiment 1-8.
  • FIG. 1 is a schematic cross-sectional view showing the scroll compressor 100 according to the first embodiment.
  • the scroll compressor 100 is applied to a refrigerating cycle device 200 described later, which is used for refrigerating or air conditioning applications such as a refrigerator or a freezer, a vending machine, an air conditioner, a refrigerating device, and a water heater.
  • the scroll compressor 100 sucks in the refrigerant circulating in the refrigerating circuit of the refrigerating cycle device 200, compresses it, and discharges it in a high temperature and high pressure state.
  • the scroll compressor 100 includes a shell 2, an oil pump 3, a motor 4, a compression mechanism unit 5, a frame 6, and a shaft unit 7. Further, the scroll compressor 100 includes a suction pipe 11, a discharge pipe 12, a discharge chamber 13, an old dam ring 15, a slider 16, a sleeve 17, a first balancer 18, a second balancer 19, and a subframe. 20 and an oil drain pipe 21 are provided.
  • the shell 2 constitutes the outer shell of the closed container and forms a closed space inside the shell 2.
  • the shell 2 is formed in a bottomed cylindrical shape, and an oil reservoir 3a for storing lubricating oil is provided at the inner bottom portion of the shell 2.
  • the shell 2 includes a middle shell 2c forming a cylindrical peripheral wall, a dome-shaped upper shell 2a that closes the upper opening of the middle shell 2c, and a dome-shaped lower shell 2b that closes the lower opening of the middle shell 2c.
  • an oil pump 3 Inside the shell 2, an oil pump 3, a motor 4, a compression mechanism portion 5, a frame 6, a shaft portion 7, a subframe 20, an oil drain pipe 21, and the like are housed.
  • Oil pump 3 The oil pump 3 is housed in the shell 2 and sucks oil from the oil sump 3a.
  • the oil pump 3 is provided at the lower part in the shell 2. Then, the oil pump 3 supplies the oil sucked up from the oil sump 3a to the lubricated portion so as to lubricate the lubricated portion such as the bearing portion inside the scroll compressor 100.
  • the oil that has been sucked up by the oil pump 3 and lubricated the oscillating bearing 8c is stored in, for example, the internal space 6d of the frame 6 and then passes through the radial oil supply groove 6c provided in the thrust bearing 6b and is an old dam. It flows into the ring space 15b and lubricates the old dam ring 15.
  • An oil drain pipe 21 is connected to the old dam ring space 15b, and oil is returned to the oil sump 3a through the oil drain pipe 21.
  • the motor 4 is installed between the frame 6 and the subframe 20 inside the shell 2 to rotate the shaft portion 7.
  • the motor 4 has a rotor 4a and a stator 4b.
  • the rotor 4a is provided on the inner peripheral side of the stator 4b and is attached to the shaft portion 7.
  • the rotor 4a rotates on its axis to rotate the shaft portion 7.
  • the stator 4b rotates the rotor 4a by electric power supplied from an inverter (not shown).
  • the compression mechanism unit 5 is arranged in the shell 2 and compresses a fluid (for example, a refrigerant) sucked into the shell 2 from the suction pipe 11.
  • the compression mechanism unit 5 is housed in the shell 2 and constitutes a compression chamber 5a for compressing the refrigerant, and the compression mechanism unit 5 is formed with a discharge port 32 for discharging the refrigerant compressed in the compression chamber 5a.
  • the compression mechanism unit 5 includes a fixed scroll 30 fixed to the shell 2 and a swing scroll 40 that swings (that is, revolves) with respect to the fixed scroll 30.
  • the compression mechanism unit 5 forms a compression chamber 5a by the fixed scroll 30 and the swing scroll 40.
  • the fixed scroll 30 is fixed to, for example, a frame 6 fixedly supported in the shell 2 by bolts or the like.
  • the fixed scroll 30 is arranged so as to face the swing scroll 40.
  • the fixed scroll 30 has a base plate 30a and a spiral portion 31 extending downward on the lower surface of the base plate 30a.
  • the spiral portion 31 projects from the wall surface of the base plate 30a facing the rocking scroll 40 toward the rocking scroll 40, and the cross section parallel to the base plate 30a is a spiral-shaped protrusion.
  • the base plate 30a is formed in a plate shape.
  • a discharge port 32 for discharging the refrigerant compressed in the compression chamber 5a is formed so as to penetrate the base plate 30a.
  • the discharge port 32 is a through hole for communicating the discharge chamber 13 and the compression chamber 5a.
  • a discharge valve mechanism 50 is provided at the outlet portion 32a which is the opening end on the outlet side of the refrigerant.
  • the discharge valve mechanism 50 prevents the backflow of the refrigerant discharged from the outlet portion 32a of the discharge port 32. The details of the discharge valve mechanism 50 will be described later.
  • the swing scroll 40 performs a revolution rotation motion, in other words, a swing motion with respect to the fixed scroll 30, and the rotation motion is regulated by the old dam ring 15.
  • the swing scroll 40 has a base plate 40a and a spiral portion 41 extending upward on the upper surface of the base plate 40a.
  • the spiral portion 41 projects from the wall surface of the base plate 40a facing the fixed scroll 30 toward the fixed scroll 30, and the cross section parallel to the base plate 40a is a spiral-shaped protrusion.
  • the base plate 40a is a disk-shaped member, and swings in the frame 6 due to the rotation of the shaft portion 7.
  • the fixed scroll 30 and the swing scroll 40 are arranged in a state where the spiral portion 31 and the spiral portion 41 face each other on the surfaces facing each other, and the spiral portion 31 and the spiral portion 41 are meshed with each other.
  • a compression chamber 5a is formed in the space where the spiral portion 31 of the fixed scroll 30 and the spiral portion 41 of the swing scroll 40 mesh with each other.
  • the compression chamber 5a is a space surrounded by the base plate 40a and the spiral portion 41 of the swing scroll 40 and the base plate 30a and the spiral portion 31 of the fixed scroll 30.
  • the frame 6 is formed in a cylindrical shape, the outer peripheral portion thereof is fixed to the shell 2, and the inner peripheral portion accommodates the compression mechanism portion 5.
  • the frame 6 holds the swing scroll 40 of the compression mechanism unit 5. Further, the frame 6 rotatably supports the shaft portion 7 via the main bearing 8a.
  • a suction port 6a is formed on the frame 6. The gaseous refrigerant existing in the shell 2 flows into the compression mechanism portion 5 through the suction port 6a.
  • the shaft portion 7 is connected to the motor 4 and the swing scroll 40, respectively, and transmits the rotational force of the motor 4 to the swing scroll 40.
  • the shaft portion 7 is rotatably supported by a main bearing 8a provided on the frame 6 and an auxiliary bearing 8b provided on the subframe 20 described later.
  • An oil passage 7a is formed inside the shaft portion 7 to allow the oil sucked up by the oil pump 3 to flow upward.
  • the shaft portion 7 has an eccentric portion 7b whose central axis is eccentric at the upper portion.
  • the suction pipe 11 is a pipe that sucks the gas-state refrigerant into the shell 2.
  • the suction pipe 11 is provided on the side wall portion of the shell 2 and is connected to the middle shell 2c.
  • the discharge pipe 12 is a pipe that discharges the refrigerant compressed by the compression mechanism unit 5 to the outside of the shell 2.
  • the discharge pipe 12 is provided on the upper part of the shell 2 and is connected to the upper shell 2a.
  • the discharge chamber 13 is a space provided above the compression mechanism portion 5, and is a space surrounded by the upper shell 2a of the shell 2 and the compression mechanism portion 5.
  • the discharge chamber 13 accommodates the refrigerant compressed by the compression mechanism unit 5 and discharged from the compression mechanism unit 5.
  • the old dam ring 15 is arranged on a thrust surface which is a surface opposite to the upper surface on which the spiral portion 41 of the swing scroll 40 is formed, and prevents the rotation scroll of the swing scroll 40 from rotating.
  • the old dam ring 15 functions to prevent the rolling motion of the swinging scroll 40 and to enable the swinging motion of the swinging scroll 40.
  • claws are formed so as to project so as to be orthogonal to each other. The claws of the old dam ring 15 are fitted into the old dam grooves (not shown) formed in the swing scroll 40 and the frame 6, respectively.
  • the slider 16 is a cylindrical member attached to the outer peripheral surface of the upper portion of the shaft portion 7.
  • the slider 16 is arranged at a position facing the inner side surface of the tubular boss portion 42 provided at the lower part of the swing scroll 40.
  • the swing scroll 40 is attached to the shaft portion 7 via the slider 16. As a result, the swing scroll 40 rotates with the rotation of the shaft portion 7.
  • a swing bearing 8c serving as a bearing is provided between the swing scroll 40 and the slider 16.
  • the sleeve 17 is a cylindrical member provided between the frame 6 and the main bearing 8a.
  • the sleeve 17 absorbs the inclination of the frame 6 and the shaft portion 7.
  • the first balancer 18 is attached to the shaft portion 7.
  • the first balancer 18 is arranged between the frame 6 and the rotor 4a.
  • the first balancer 18 offsets the imbalance caused by the swing scroll 40 and the slider 16.
  • the first balancer 18 is housed in the balancer cover 18a.
  • the second balancer 19 is attached to the shaft portion 7.
  • the second balancer 19 is arranged between the rotor 4a and the subframe 20 and is attached to the lower surface of the rotor 4a.
  • the second balancer 19 offsets the imbalance caused by the swing scroll 40 and the slider 16.
  • the subframe 20 is provided below the motor 4 inside the shell 2 and rotatably supports the shaft portion 7 via the auxiliary bearing 8b.
  • the oil drain pipe 21 is a pipe connecting the space between the frame 6 and the swing scroll 40 and the space between the frame 6 and the subframe 20.
  • the oil drain pipe 21 causes excess oil of the oil flowing in the space between the frame 6 and the swing scroll 40 to flow out into the space between the frame 6 and the subframe 20.
  • the oil that has flowed out into the space between the frame 6 and the subframe 20 passes through the subframe 20 and is returned to the oil sump 3a.
  • the gas-state refrigerant sucked into the shell 2 from the suction pipe 11 due to the swinging motion of the swinging scroll 40 is formed between the spiral portion 31 of the fixed scroll 30 and the spiral portion 41 of the swinging scroll 40. It is taken into the compression chamber 5a and compressed toward the center. Then, the compressed refrigerant is discharged by opening the discharge valve mechanism 50 from the discharge port 32 formed in the fixed scroll 30, and is discharged from the discharge pipe 12 to the outside of the scroll compressor 100, that is, to the refrigerant circuit.
  • the imbalance caused by the movement of the swing scroll 40 and the old dam ring 15 is balanced by the first balancer 18 attached to the shaft portion 7 and the second balancer 19 attached to the rotor 4a. .. Further, the lubricating oil stored in the lower part of the shell 2 is supplied from the oil passage 7a provided in the shaft portion 7 to each sliding portion such as the main bearing 8a, the auxiliary bearing 8b and the thrust surface.
  • FIG. 2 is a schematic cross-sectional view showing a discharge valve mechanism 50 of the scroll compressor 100 according to the first embodiment.
  • the discharge valve mechanism 50 will be described with reference to FIGS. 1 and 2.
  • the discharge valve mechanism 50 is provided in the compression mechanism portion 5 on the side facing the discharge chamber 13, and has a function of opening and closing the discharge port 32. More specifically, as shown in FIG. 2, the discharge valve mechanism 50 is provided on the discharge chamber 13 side of the fixed scroll 30.
  • the surface of the fixed scroll 30 on which the discharge valve mechanism 50 is provided on the discharge chamber 13 side is a flat surface.
  • the discharge valve mechanism 50 has one reed valve 51 and a valve seat 52 on which the reed valve 51 is seated. Further, the discharge valve mechanism 50 includes a valve retainer 53.
  • the lead valve 51 opens and closes the outlet portion 32a of the discharge port 32 according to the discharge pressure of the refrigerant.
  • the lead valve 51 is provided on the discharge chamber 13 side of the compression mechanism portion 5, and is arranged so as to cover the outlet portion 32a which is the opening end on the outlet side of the discharge port 32.
  • the lead valve 51 is a long plate-shaped member, and has a fixed portion 51a attached to the fixed scroll 30 of the compression mechanism portion 5 and a tip portion 51b which is a free end.
  • the lead valve 51 is formed so as to connect the fixing portion 51a and the tip portion 51b in the longitudinal direction and extend straight. Note that “straight” is not limited to the case of “straight” strictly, but also includes the case of being almost straight.
  • the fixing portion 51a located at one end in the longitudinal direction of the lead valve 51 is attached to the fixing scroll 30 by the fixing tool 54 together with the valve holding 53.
  • the fixative 54 is, for example, a screw member.
  • the fixing portion 51a of the lead valve 51 is fixed to the surface portion 30a1 on the discharge chamber 13 side of the base plate 30a constituting the fixed scroll 30.
  • the tip portion 51b located at the other end is a free end portion located at the tip of the lead valve 51 extending in the longitudinal direction from the fixing portion 51a and not fixed to other members. be.
  • the tip portion 51b of the lead valve 51 sits on the valve seat 52, covers the discharge port 32, and serves as a sealing portion that separates the space on the discharge chamber 13 side from the space on the compression chamber 5a side.
  • the lead valve 51 closes the valve seat 52 when the tip portion 51b is seated on the valve seat 52.
  • the lead valve 51 comes into contact with at least a part of the valve support portion 52b, which will be described later, and the annular portion 52a.
  • FIG. 3 is a top view conceptually showing an enlarged valve seat 52 portion of the scroll compressor 100 according to the first embodiment.
  • the valve seat 52 is a portion that receives the lead valve 51, which is a valve body, when the discharge port 32 is closed.
  • the valve seat 52 is provided on the surface of the fixed scroll 30 on the discharge chamber 13 side, and is provided at the outlet portion 32a of the discharge port 32 which is the opening end on the outlet side of the refrigerant.
  • the valve seat 52 is provided on the inner peripheral side of the annular portion 52a formed so as to form the edge of the opening of the outlet portion 32a and the annular portion 52a, and is provided on the inner peripheral side of the annular portion 32a. It has a valve support portion 52b that partitions the opening and constitutes a plurality of valve seat holes 52d that are through holes. The surfaces of the annular portion 52a and the valve support portion 52b on the discharge chamber 13 side are formed flush with each other, but the configuration is not limited to this.
  • the annular portion 52a is a wall portion formed in an annular shape in a plan view of the shaft portion 7 in FIG. 1 in the axial direction, and is formed in a cylindrical shape.
  • a groove 33 is formed on the outer peripheral side of the annular portion 52a.
  • the groove portion 33 is a groove formed in an annular shape in a plan view of the shaft portion 7 in the axial direction, and is a portion in which the surface portion 30a1 of the fixed scroll 30 is recessed toward the compression chamber 5a.
  • the annular portion 52a may be a wall portion formed in an annular shape in a plan view of the shaft portion 7 in FIG. 1, and is not limited to an annular portion.
  • the valve support portion 52b is formed in a rod shape so as to bridge the facing wall portion inside the annular portion 52a.
  • the valve support portion 52b is formed in an I-shape in a plan view of the shaft portion 7 in the axial direction.
  • the valve support portion 52b has at least a part of the valve support portion 52b in contact with the lead valve 51.
  • the valve support portion 52b is provided so as to be orthogonal to the longitudinal direction of the lead valve 51.
  • the valve support portion 52b may have a portion that supports the lead valve 51 near the center of the opening of the outlet portion 32a, and the extending direction of the valve support portion 52b may be parallel to the longitudinal direction of the lead valve 51 and intersect. It may be in the direction.
  • the valve support portion 52b may have a portion that supports the lead valve 51 in the opening of the outlet portion 32a, and a portion that supports the lead valve 51 in a place other than the vicinity of the center of the opening in the opening of the outlet portion 32a. There may be.
  • the valve support portion 52b may be any as long as it partitions the opening of the outlet portion 32a and forms a plurality of valve seat holes 52d inside the annular portion 52a. Further, the valve support portion 52b may have a structure in which at least a part of the valve support portion 52b comes into contact with the lead valve 51 when the lead valve 51 is seated on the valve seat 52. Therefore, the structure of the valve support portion 52b is not limited to the rod-shaped structure as shown in FIG.
  • valve seat holes 52d are formed in the valve seat 52.
  • the valve seat hole 52d is formed by the valve seat 52 at the outlet portion 32a, which is the open end on the outlet side of the discharge port 32.
  • the valve seat hole 52d is formed by being surrounded by the annular portion 52a and the valve support portion 52b.
  • the valve seat hole 52d is a through hole through which the refrigerant discharged from the discharge port 32 passes.
  • the valve seat hole 52d is formed in a fan shape, for example, as shown in FIG. 3 in a plan view of the shaft portion 7 in the axial direction.
  • the lead valve 51 sits on the valve seat 52 so as to close the valve seat hole 52d.
  • valve seat holes 52d formed is not limited to two.
  • the valve seat 52 may be formed with two or more valve seat holes 52d.
  • the discharge valve mechanism 50 is provided with a valve support portion 52b so that two or more valve seat holes 52d are formed in the discharge port 32 opened in the central portion, so that the valve seat 52 and the lead valve 51 are seated. Will increase.
  • FIG. 4 is an enlarged view of the vicinity of the outlet portion 32a of the discharge valve mechanism 50 shown in FIG.
  • the valve support portion 52b does not need to be provided over the entire thickness of the base plate 30a constituting the fixed scroll 30.
  • the thickness of the base plate 30a is the thickness of the base plate 30a in the axial direction S of the shaft portion 7 in FIG. 1.
  • the thickness L1 of the valve support portion 52b may have a length of 1/5 to 1/15 of the thickness L of the base plate 30a. If the thickness L1 of the valve support portion 52b is long, the pressure loss increases, and if it is short, the reliability of supporting the lead valve 51 decreases.
  • FIG. 5 is an enlarged view conceptually showing a first modification of the valve support portion 52b according to the first embodiment.
  • the valve support portion 52b may have a support tip portion 52b1.
  • the support tip portion 52b1 constitutes the lower end portion of the valve support portion 52b, and is a portion located at the end portion on the compression chamber 5a side in the axial direction S of the shaft portion 7 of FIG.
  • the support tip portion 52b1 may be formed in a sharp shape on the space side of the compression chamber 5a.
  • the support tip portion 52b1 is formed in a sharp shape in a vertical cross section along the axial direction S of the shaft portion 7, and the tip of the support tip portion 52b1 forms the apex of the mountain. It may be formed in a triangular shape.
  • the valve support portion 52b can reduce the pressure loss of the high-pressure gas from the compression chamber 5a toward the discharge chamber 13.
  • FIG. 6 is an enlarged view conceptually showing a second modification of the valve support portion 52b according to the first embodiment.
  • the valve support portion 52b is provided at an angle so that the gas from the compression chamber 5a toward the discharge chamber 13 is directed toward the tip portion 51b side of the lead valve 51, so that the lead valve 51 can be easily opened. It may be formed so as to become.
  • the valve support portion 52b may be provided so as to be inclined so that the upper end portion 52b12 is located closer to the tip portion 51b of the lead valve 51 than the lower end portion 52b11.
  • the upper end portion 52b12 is the end portion of the valve support portion 52b on the discharge chamber 13 side
  • the lower end portion 52b11 is the end portion of the valve support portion 52b on the compression chamber 5a side.
  • the valve support portion 52b is provided so as to be inclined with respect to the extending direction of the flow path of the discharge port 32.
  • the valve retainer 53 is a long plate-shaped member thicker than the lead valve 51, and has a fixed end portion 53a attached to the compression mechanism portion 5 and a tip portion 53b which is a free end. have.
  • the valve retainer 53 connects the fixed end portion 53a and the tip portion 53b in the longitudinal direction, and bends the tip portion 53b toward the discharge chamber 13.
  • the valve retainer 53 supports the reed valve 51 from the back surface when the reed valve 51 is opened, and protects the reed valve 51 from being deformed more than necessary.
  • the pressure in the compression chamber 5a increases.
  • the tip portion 51b of the lead valve 51 is pushed up, the lead valve 51 is warped, and the tip portion 51b is the valve seat 52.
  • the discharge port 32 is opened by moving away from.
  • the discharge port 32 is opened when the lead valve 51 is separated from the valve seat 52.
  • the lead valve 51 which is separated from the valve seat 52 and has the discharge port 32 opened, is supported behind by a valve retainer 53 to prevent damage.
  • FIG. 7 is a schematic cross-sectional view showing a discharge valve mechanism 50L of the scroll compressor 100L according to a comparative example.
  • the scroll compressor 100L according to the comparative example does not have the valve support portion 52b on the valve seat 52.
  • the scroll compressor 100L according to the comparative example bends inward of the discharge port 32 when the lead valve 51 is seated on the valve seat 52.
  • FIG. 8 is a schematic cross-sectional view showing the discharge valve mechanism 50 of the scroll compressor 100 according to the first embodiment.
  • the valve seat 52 of the scroll compressor 100 according to the first embodiment is provided on the inner peripheral side of the annular portion 52a formed so as to form the edge of the opening of the outlet portion 32a, and the outlet portion 32a. It has a valve support portion 52b that partitions the opening of the valve seat hole 52d and constitutes a plurality of valve seat holes 52d.
  • the lead valve 51 comes into contact with at least a part of the valve support portion 52b provided in the discharge port 32 and the annular portion 52a.
  • the reed valve 51 Since the reed valve 51 abuts on the valve seat 52 not only at the position facing the edge of the outlet portion 32a but also at a plurality of positions, the amount of deflection of the reed valve 51 can be dispersed, and the load when the reed valve 51 is seated can be used. The amount of bending can be suppressed. As a result, since the amount of bending of the reed valve 51 is suppressed, the reed valve 51 is prevented from being destroyed by the bending, and the reliability of the strength of the reed valve 51 can be ensured.
  • the scroll compressor 100 can cope with an increase in the diameter of the discharge port due to the above structure.
  • valve seat hole 52d of the valve seat 52 can be formed by casting, circular cutting, forging, or the like, the valve seat 52 can be easily manufactured.
  • the discharge valve mechanism 50 has a structure in which the lead valve 51 is seated only at a position facing the edge portion of the outlet portion 32a, and the valve support portion 52b causes a large deflection of the lead valve 51.
  • the lead valve 51 can be supported at this position. Therefore, the scroll compressor 100 can narrow the width of the annular portion 52a of the valve seat 52 without deteriorating the reliability of the lead valve 51. Since the scroll compressor 100 can reduce the oil film breakage resistance between the lead valve 51 and the valve seat 52 by the configuration, the overcompression loss at the valve opening timing can be reduced.
  • the scroll compressor 100 Since the scroll compressor 100 has the valve support portion 52b, the annular portion 52a of the valve seat 52 does not excessively expand the seating area of the valve seat 52, and the lead valve 51 and the valve seat 52 at the time of valve opening do not expand too much. The oil film break resistance can be reduced, and the overcompression loss at the valve opening timing can be reduced. Further, since the scroll compressor 100 has the valve support portion 52b, the annular portion 52a of the valve seat 52 does not excessively expand the seating area of the valve seat 52, and the amount of valve deformation and the lead when the lead valve 51 is seated is increased. The increase in stress generated in the valve 51 can be suppressed to a minimum.
  • the reliability of the strength of the reed valve 51 can be improved by increasing the thickness of the reed valve 51. Conceivable. However, increasing the thickness of the reed valve makes it difficult for the reed valve 51 to open, resulting in pressure loss and deterioration of the performance of the scroll compressor 100L. Further, increasing the thickness of the lead valve 51 also leads to an increase in cost.
  • the amount of bending of the lead valve 51 can be suppressed by providing the valve support portion 52b on the valve seat 52, and the reliability of the strength can be improved without changing the thickness of the lead valve 51. Can be secured.
  • valve support portion 52b has a tip portion having a sharp tip on the side where the compression chamber 5a is provided. Therefore, the valve support portion 52b can reduce the pressure loss of the high-pressure gas from the compression chamber 5a to the discharge chamber 13 due to the shape of the support tip portion 52b1.
  • valve support portion 52b is provided so as to be inclined so that the upper end portion 52b12 is located on the side where the tip portion 51b of the lead valve 51 is arranged rather than the lower end portion 52b11.
  • the gas directed from the compression chamber 5a to the discharge chamber 13 is directed toward the tip portion 51b side of the lead valve 51 more due to the configuration, so that the valve support portion 52b is not provided with an inclination as compared with the case where the valve support portion 52b is not provided at an angle.
  • the lead valve 51 can be easily opened.
  • FIG. 9 is a top view showing the valve seat 52 of the scroll compressor 100 according to the second embodiment.
  • FIG. 9 in order to show the structure of the valve seat 52, it is shown in a state where the lead valve 51 is transmitted by a dotted line.
  • the parts having the same configuration as the scroll compressor 100 of FIGS. 1 to 8 are designated by the same reference numerals and the description thereof will be omitted, and the scroll of FIGS. 1 to 8 will be omitted.
  • a feature portion different from that of the compressor 100 will be described.
  • the valve seat 52 is formed so that the width of the wall differs depending on the position where the lead valve 51 is seated.
  • the valve seat 52 is formed so that the width of the valve seat 52 in the horizontal direction is different between the arrangement side of the tip portion 51b of the lead valve 51 and the arrangement side of the fixed portion 51a.
  • the valve seat 52 is formed so that the width of the annular portion 52a in the horizontal direction becomes smaller toward the tip end direction P of the lead valve 51.
  • the valve seat 52 is formed so that the width of the annular portion 52a in the horizontal direction becomes smaller in the direction from the fixed portion 51a of the lead valve 51 toward the tip portion 51b.
  • the horizontal direction is a direction perpendicular to the axial direction of the shaft portion 7.
  • the width of the annular portion 52a on one side with respect to the central portion C of the opening of the annular portion 52a is wider than the width of the annular portion 52a on the other side with respect to the central portion C of the opening of the annular portion 52a. Is also formed to be small.
  • the valve seat 52 is formed so that the horizontal width of the annular portion 52a becomes smaller in the direction from the fixed portion 51a of the lead valve 51 toward the tip portion 51b. According to this configuration, since the lead valve 51 opens from the tip portion 51b side when the valve is opened, the width of the valve seat 52 is the same on the tip portion 51b side and the fixed portion 51a side. In comparison, the lead valve 51 is easier to open. Therefore, the scroll compressor 100 causes an overcompression loss when the lead valve 51 is opened, as compared with the case where the width of the valve seat 52 is the same on the tip portion 51b side and the fixed portion 51a side. Can be reduced.
  • the tip portion 51b side of the reed valve 51 has an oil film between the reed valve 51 and the valve seat 52 as compared with the fixed portion 51a of the reed valve 51.
  • the scroll compressor 100 has the oil film breaking resistance on the tip portion 51b side as compared with the case where the width of the valve seat 52 is the same on the tip portion 51b side and the fixing portion 51a side due to the above configuration. It can be reduced and the timing of valve opening can be optimized.
  • FIG. 10 is a top view showing the valve seat 52 of the scroll compressor 100 according to the third embodiment.
  • FIG. 10 in order to represent the structure of the valve seat 52, it is represented in a state where the lead valve 51 is transmitted by a dotted line.
  • the parts having the same configuration as the scroll compressor 100 of FIGS. 1 to 9 are designated by the same reference numerals and the description thereof will be omitted, and the scroll of FIGS. 1 to 9 will be omitted.
  • a feature portion different from that of the compressor 100 will be described.
  • the valve seat 52 is formed so that the sizes of the plurality of valve seat holes 52d are different.
  • the plurality of valve seat holes 52d have at least a first valve seat hole 52d1 and a second valve seat hole 52d2.
  • the position of the valve support portion 52b is offset from the central portion C of the opening of the annular portion 52a, and the opening area S1 of the first valve seat hole 52d1 is the second valve seat hole 52d2. It is formed so as to be larger than the opening area S2.
  • the first valve seat hole 52d1 is a through hole formed on the arrangement side of the tip portion 51b of the lead valve 51 with respect to the second valve seat hole 52d2, and the second valve seat hole 52d2 is the first valve seat hole 52d1. It is a through hole formed on the side where the fixing portion 51a of the lead valve 51 is arranged.
  • the valve support portion 52b is arranged on the fixed portion 51a side with respect to the central portion C in the opening of the annular portion 52a.
  • the opening area S1 of the first valve seat hole 52d1 is formed so as to be larger than the opening area S2 of the second valve seat hole 52d2. According to this configuration, in the scroll compressor 100, the amount of gas passing through the first valve seat hole 52d1 is larger than the amount of gas passing through the second valve seat hole 52d2, and the tip portion 51b side of the lead valve 51 is located. It is pushed up by a lot of gas with respect to the fixed portion 51a side. Therefore, in the scroll compressor 100, the lead valve 51 is more likely to open than in the case where the opening area S1 and the opening area S2 of the valve seat hole 52d are equal to each other. As a result, the scroll compressor 100 can reduce the overcompression loss at the time of opening the lead valve 51 as compared with the case where the opening area S1 and the opening area S2 of the valve seat hole 52d are equal to each other.
  • FIG. 11 is a top view showing the valve seat 52 of the scroll compressor 100 according to the fourth embodiment.
  • the parts having the same configuration as the scroll compressor 100 of FIGS. 1 to 10 are designated by the same reference numerals and the description thereof will be omitted, and the scroll of FIGS. 1 to 10 will be omitted. A feature portion different from that of the compressor 100 will be described.
  • valve support portion 52b is formed in an I-shape in a plan view of the shaft portion 7 in the axial direction, but in the fourth embodiment, the valve support portion 52b is the shaft portion 7. It is formed in a Y-shape in a plan view seen in the axial direction of.
  • valve seat 52 two valve seat holes 52d are formed in the first embodiment, but three valve seat holes 52d are formed in the fourth embodiment.
  • the valve support portion 52b is formed in a Y-shape in a plan view of the shaft portion 7 in the axial direction.
  • the valve support portion 52b of the fourth embodiment has more connection portions with the annular portion 52a than the valve support portion 52b of the first embodiment. Therefore, the valve support portion 52b of the fourth embodiment can secure the reliability of the strength as compared with the valve support portion 52b of the first embodiment.
  • FIG. 12 is a top view showing the valve seat 52 of the scroll compressor 100 according to the fifth embodiment.
  • the parts having the same configuration as the scroll compressor 100 of FIGS. 1 to 11 are designated by the same reference numerals and the description thereof will be omitted, and the scroll of FIGS. 1 to 11 will be omitted. A feature portion different from that of the compressor 100 will be described.
  • valve support portion 52b is formed in an I-shape in a plan view of the shaft portion 7 in the axial direction, but in the fifth embodiment, the valve support portion 52b is the shaft portion 7. It is formed in an X-shape in a plan view seen in the axial direction of.
  • valve seat 52 two valve seat holes 52d are formed in the first embodiment, but four valve seat holes 52d are formed in the fifth embodiment.
  • valve support portion 52b may have a valve receiving portion 52e at the central portion C of the opening of the annular portion 52a.
  • the valve receiving portion 52e is a portion where the lead valve 51 comes into contact with the annular portion 52a when the lead valve 51 is seated on the valve seat 52.
  • the valve receiving portion 52e is formed in a columnar shape, for example.
  • the portion of the valve receiving portion 52e facing the lead valve 51 in a plan view of the shaft portion 7 in the axial direction is formed in a circular shape.
  • the diameter T of the valve receiving portion 52e is formed to be larger than the width W of the supporting portion 52f.
  • the support portion 52f constitutes a portion between the valve receiving portion 52e and the annular portion 52a, and is a portion that supports the valve receiving portion 52e.
  • the valve support portion 52b may have a larger area only in the central portion in the opening of the annular portion 52a, and the other portions may have a smaller width than the central portion.
  • the valve support portion 52b is formed so that the valve receiving portion 52e, which is a portion that receives the lead valve 51, has a size of about one-third to one-seventh of the diameter R of the opening of the annular portion 52a. Is desirable. Even if the valve receiving portion 52e has a structure formed in another shape such as a square shape or another polygonal shape instead of a circular shape, the receiving portion 52e is formed in such a size. Is desirable.
  • the valve support portion 52b is formed in an X-shape in a plan view of the shaft portion 7 in the axial direction.
  • the valve support portion 52b of the fifth embodiment has more connection portions with the annular portion 52a than the valve support portion 52b of the first embodiment. Therefore, the valve support portion 52b of the fifth embodiment can secure the reliability of the strength as compared with the valve support portion 52b of the first embodiment.
  • the valve support portion 52b is formed so that the diameter T of the valve receiving portion 52e is larger than the width W of the support portion 52f at the portion facing the lead valve 51.
  • the diameter T of the valve receiving portion 52e is formed to be larger than the width W of the supporting portion 52f, so that the area of the portion with which the lead valve 51 abuts can be secured.
  • the width W of the support portion 52f is formed to be smaller than the diameter T of the valve receiving portion 52e, so that the opening area of the valve seat hole 52d can be secured.
  • FIG. 13 is a schematic cross-sectional view showing the discharge valve mechanism 50 of the scroll compressor 100 according to the sixth embodiment.
  • the parts having the same configuration as the scroll compressor 100 of FIGS. 1 to 12 are designated by the same reference numerals and the description thereof will be omitted, and the scroll of FIGS. 1 to 12 will be omitted. A feature portion different from that of the compressor 100 will be described.
  • annular portion 52a and the valve support portion 52b are formed so that the surfaces on the discharge chamber 13 side are flush with each other, but in the sixth embodiment, the annular portion 52a and the valve support portion 52b are discharged. The surface on the chamber 13 side is not formed flush with each other.
  • the valve support portion 52b is arranged on the forming side of the compression chamber 5a with respect to the annular portion 52a. More specifically, the support surface 52g of the valve support portion 52b facing the reed valve 51 is arranged on the forming side of the compression chamber 5a with respect to the support surface 52h of the annular portion 52a facing the reed valve 51. According to the sixth embodiment, the height of the wall surface of the valve support portion 52b that divides the opening of the valve seat 52 is the discharge chamber of the annular portion 52a if the height that suppresses the bending of the lead valve 51 can be secured. It does not have to be formed at the same height as the surface on the 13 side.
  • the valve support portion 52b may be recessed on the forming side of the compression chamber 5a instead of being flush with the support surface 52h of the annular portion 52a which is the sealing surface, to some extent.
  • the reed valve 51 bends to some extent when the valve is closed, but the contact area between the reed valve 51 and the gas becomes large, so that the valve opening can be improved.
  • a configuration in which the valve support portion 52b projects from the support surface 52h of the annular portion 52a, which is the sealing surface, toward the discharge chamber 13 is not desirable because the sealing property between the lead valve 51 and the valve seat 52 deteriorates.
  • the support surface 52g which is the surface of the valve support portion 52b on the formation side of the discharge chamber 13 is provided on the formation side of the compression chamber 5a, rather than the support surface 52h, which is the surface of the annular portion 52a, on the formation side of the discharge chamber 13. Has been done. According to this configuration, the valve seat 52 can reduce the surface area of the wall surface with which the compressed refrigerant gas comes into contact, which is increased by dividing the discharge port 32, and can reduce the pressure loss.
  • FIG. 14 is a conceptual diagram showing a valve seat 52 of the scroll compressor 100 according to the seventh embodiment.
  • FIG. 15 is a schematic vertical sectional view showing a valve seat 52 of the scroll compressor 100 according to the seventh embodiment.
  • the parts having the same configuration as the scroll compressor 100 of FIGS. 1 to 13 are designated by the same reference numerals and the description thereof will be omitted, and the scroll of FIGS. 1 to 13 will be omitted. A feature portion different from that of the compressor 100 will be described.
  • the valve seat 52 of the first embodiment has a structure in which the annular portion 52a and the valve support portion 52b are integrally formed, whereas the valve seat 52 of the seventh embodiment has the annular portion 52a and the valve support portion. It is a structure in which 52b and 52b are formed separately.
  • a recess 34 is provided in the outlet portion 32a of the discharge port 32.
  • the recess 34 is formed so that the surface portion 30a1 of the fixed scroll 30 is recessed along the discharge port 32, and is recessed from the formation side of the discharge chamber 13 toward the formation side of the compression chamber 5a.
  • the recess 34 is formed on the inner peripheral side of the annular portion 52a.
  • the bottom portion 34a of the recess 34 is formed in an annular shape in a plan view, and a step is formed between the bottom portion 34a and the surface portion 30a1 of the fixed scroll 30.
  • the inner diameter of the recess 34 is larger than the inner diameter of the discharge port 32 between the recess 34 and the compression chamber 5a.
  • the valve support portion 52b is fitted on the inner peripheral side of the recess 34 and is arranged inside the recess 34.
  • the valve support portion 52b is fixed to the outlet portion 32a of the fixed scroll 30 by a fixing member 35 such as a screw.
  • the valve support portion 52b is arranged on the inner peripheral side of the annular portion 52a and constitutes the valve seat 52 together with the annular portion 52a.
  • the valve support portion 52b is provided on the inner peripheral side of the outer peripheral portion 52b21 formed in an annular shape and the outer peripheral portion 52b21, and partitions the opening of the outlet portion 32a to form a plurality of valve seat holes 52d which are through holes. It has a portion 52b22 and a portion 52b22.
  • the outer peripheral portion 52b21 may have a shape that fits the annular portion 52a in a plan view of the shaft portion 7 in FIG. 1 in the axial direction.
  • the outer peripheral portion 52b21 may be an annular shape other than the annular shape, and is not limited to the annular shape.
  • the inner diameter of the outer peripheral portion 52b21 is defined as the inner diameter r1
  • the inner diameter of the discharge port 32 is defined as the inner diameter r2.
  • the inner diameter r1 is also the inner diameter of the valve seat 52. It is desirable that the inner diameter r1 of the outer peripheral portion 52b21 is larger than the inner diameter r2 of the discharge port 32 (inner diameter r1> inner diameter r2). With this configuration, it is possible to prevent the high-pressure gas discharged from the discharge port 32 from colliding with the peripheral portion of the valve seat 52 such as the outer peripheral portion 52b21, and it is possible to reduce the compression loss of the high-pressure gas.
  • the partition portion 52b22 is formed in a rod shape so as to bridge the facing wall portion inside the outer peripheral portion 52b21.
  • the partition portion 52b22 is formed in an I-shape in a plan view of the shaft portion 7 in the axial direction, but is not limited to the configuration thereof, and is not limited to the configuration, for example, a Y-shape or an X-shape. It may be in shape.
  • the valve seat 52 of the seventh embodiment is formed with two valve seat holes 52d, but the number of valve seat holes 52d is not limited to two.
  • valve seat 52 of the seventh embodiment the annular portion 52a and the valve support portion 52b are formed separately. According to this configuration, the processing of the outlet portion 32a of the fixed scroll 30 is easy, and the processing time of the fixed scroll 30 does not increase, so that an increase in manufacturing cost can be prevented. Further, according to the configuration, the valve seat 52 can be easily machined, and for example, it becomes easy to form the valve seat 52 so that the inner diameter r1 is larger than the inner diameter r2.
  • the scroll compressor 100 can reduce the surface area of the wall surface where the compressed refrigerant gas comes into contact with the valve seat 52, and the refrigerant gas can be reduced. Pressure loss can be reduced.
  • FIG. 16 is a schematic cross-sectional view showing a discharge valve mechanism 50 of the scroll compressor 100 according to the eighth embodiment.
  • FIG. 17 is an enlarged top view conceptually showing the valve seat 52 portion of the scroll compressor 100 according to the eighth embodiment.
  • the parts having the same configuration as the scroll compressor 100 of FIGS. 1 to 15 are designated by the same reference numerals and the description thereof will be omitted, and the scroll of FIGS. 1 to 15 will be omitted. A feature portion different from that of the compressor 100 will be described.
  • the discharge valve mechanism 50 may use a float valve 151 instead of the lead valve 51.
  • the discharge valve mechanism 50 can adopt the float valve 151 instead of the lead valve 51 when there is no space for arranging the lead valve 51 in the radial direction on the discharge chamber 13 side of the fixed scroll 30.
  • the configuration when the float valve 151 is used instead of the lead valve 51 in the discharge valve mechanism 50 will be described.
  • the discharge valve mechanism 50 has one float valve 151 and a valve seat 52 on which the float valve 151 is seated. Further, the discharge valve mechanism 50 includes a float valve retainer 153 having a top plate portion 153c arranged inside the discharge chamber 13 at intervals from the outlet portion 32a so as to face the valve seat 52, and a top plate portion. It has a compression spring 155 provided between the 153c and the float valve 151.
  • the float valve 151 opens and closes the outlet portion 32a of the discharge port 32 according to the discharge pressure of the refrigerant.
  • the float valve 151 opens the opening of the outlet portion 32a away from the valve seat 52 by the discharge gas generated by the compression operation of the scroll compressor 100, and the suction generated in the scroll compression process, the weight of the float valve 151, and the compression spring 155. It is seated on the valve seat 52 by the spring force.
  • the float valve 151 is provided on the discharge chamber 13 side of the compression mechanism portion 5, and is arranged so as to cover the outlet portion 32a which is the opening end on the outlet side of the discharge port 32.
  • the float valve 151 is a plate-shaped member. Although the float valve 151 is formed in a circular shape in FIG. 17, it is not limited to the shape as long as the valve seat surface of the valve seat 52 can be sealed.
  • the float valve 151 has a compression spring 155 attached to one surface in the direction in which the flow path of the discharge port 32 (see FIG. 1) extends, and the other surface is seated on the valve seat 52 to form a valve seat 52. Contact.
  • the float valve 151 closes the valve seat 52 when seated on the valve seat 52.
  • the float valve 151 comes into contact with at least a part of the valve support portion 52b and the annular portion 52a.
  • the float valve 151 is arranged so as to be movable between the top plate portion 153c and the valve seat 52, and is pressed against the valve seat 52 by the urging force of the compression spring 155.
  • the float valve retainer 153 supports the float valve 151.
  • the float valve retainer 153 is formed in a cylindrical shape so that the float valve 151 can move up and down, but on the side wall so that the discharge gas discharged from the discharge port 32 is not blocked inside the float valve retainer 153. An opening is formed.
  • the float valve retainer 153 may be any as long as it supports the float valve 151, and its form is not limited to the tubular shape.
  • the float valve retainer 153 has a fixing portion 153a, a side wall portion 153b, and a top plate portion 153c.
  • the fixing portion 153a is a portion attached to the fixing scroll 30 of the compression mechanism portion 5 by, for example, a fixing tool 154 such as a screw member.
  • the side wall portion 153b is a wall portion provided so as to extend between the fixing portion 153a and the top plate portion 153c, and the top plate portion 153c is arranged above the outlet portion 32a.
  • the top plate portion 153c is arranged inside the discharge chamber 13 at intervals from the outlet portion 32a so as to face the valve seat 52.
  • the top plate portion 153c is connected to the float valve 151 via a compression spring 155, and supports the float valve 151 via the compression spring 155.
  • the compression spring 155 is a compression spring that receives a load in the compression direction, compresses it, and utilizes a reaction force, and presses the float valve 151 against the valve seat 52 by using the compressed reaction force. Further, the compression spring 155 receives the load in the compression direction by the float valve 151 when the float valve 151 is pushed up by the high-pressure gas protruding from the discharge port 32, and uses the compressed reaction force to valve the float valve 151. Press in the direction of pressing against the seat 52.
  • the valve support portion 52b is inclined with respect to the extending direction of the flow path of the discharge port 32 as in the second modification of the valve support portion 52b according to the first embodiment. (See FIG. 6).
  • the float valve 151 does not have a configuration in which the valve opens from the tip portion 51b. Therefore, when the outlet portion 32a is viewed in the vertical direction, the valve support portion 52b is tilted, that is, the valve support portion 52b.
  • the direction of extension is not limited.
  • the annular portion 52a may be formed in the same manner as the annular portion 52a according to the second embodiment (see FIG. 9). That is, in the annular portion 52a, the width of the annular portion 52a on one side with respect to the central portion C of the opening of the annular portion 52a is the width of the annular portion 52a on the other side with respect to the central portion C of the opening of the annular portion 52a. It may be formed so as to be smaller than the width.
  • the float valve 151 does not have a configuration in which the valve opens from the tip portion 51b, so that one side of the annular portion 52a having a small width in the circumferential direction centered on the central portion C of the opening of the annular portion 52a.
  • the position of the annular portion 52a and the other side having a large width is not limited.
  • the plurality of valve seat holes 52d may be formed in the same manner as the plurality of valve seat holes 52d according to the third embodiment (see FIG. 10). That is, in the scroll compressor 100 according to the eighth embodiment, the position of the valve support portion 52b is offset from the central portion C of the opening of the annular portion 52a, and the opening area S1 of the first valve seat hole 52d1 is the second valve seat hole. It may be formed so as to be larger than the opening area S2 of 52d2.
  • the first valve seat hole 52d1 is a through hole formed on one side of the central portion C of the opening of the annular portion 52a, and the second valve seat hole 52d2 is formed in the central portion C of the opening of the annular portion 52a.
  • the float valve 151 does not have a configuration in which the valve opens from the tip portion 51b, so that the direction in which the position of the valve support portion 52b is offset from the central portion C of the opening of the annular portion 52a is not limited. ..
  • FIG. 18 is a schematic cross-sectional view showing the discharge valve mechanism 50R of the scroll compressor 100R according to the comparative example.
  • the scroll compressor 100R according to the comparative example does not have the valve support portion 52b on the valve seat 52.
  • the scroll compressor 100R according to the comparative example bends inward of the discharge port 32 when the float valve 151 is seated on the valve seat 52. Similar to the structure having the lead valve 51 even if the scroll compressor 100 has the float valve 151, when the scroll compressor 100 does not have the valve support portion 52b, the valve bends due to the load when the valve closes. .. When the float valve 151 does not have the valve support portion 52b, the float valve 151 bends at a place where it is not seated like the lead valve 51.
  • the float valve 151 Since the float valve 151 abuts on the valve seat 52 not only at the position facing the edge of the outlet portion 32a but also at a plurality of positions, the amount of deflection of the float valve 151 can be dispersed, and the load at the time of seating of the float valve 151 can be applied. The amount of bending can be suppressed. As a result, since the amount of bending of the float valve 151 is suppressed, the float valve 151 is prevented from being broken by the bending, and the reliability of the strength of the float valve 151 can be ensured.
  • FIG. 19 is a schematic schematic diagram showing a refrigeration cycle apparatus 200 provided with the scroll compressor 100 according to the first to eighth embodiments.
  • the refrigeration cycle device 200 includes a scroll compressor 100, a condenser 201, an expansion valve 202, and an evaporator 203.
  • the refrigerating cycle device 200 connects a scroll compressor 100, a condenser 201, an expansion valve 202, and an evaporator 203 with a refrigerant pipe to form a refrigerant circulation circuit.
  • the scroll compressor 100 is the scroll compressor 100 of the first to eighth embodiments, and compresses the low-pressure gas-phase refrigerant taken into the inside to change it into a high-temperature and high-pressure gas-phase refrigerant.
  • the high temperature and high pressure refrigerant is condensed in the condenser 201 to become a liquid.
  • the liquid refrigerant is decompressed and expanded by the expansion valve 202 to become a low-temperature low-pressure gas-liquid two-phase, and the gas-liquid two-phase refrigerant is heat-exchanged in the evaporator 203.
  • the refrigerant flowing out of the evaporator 203 is sucked into the scroll compressor 100 and becomes a high-temperature and high-pressure vapor-phase refrigerant.
  • the refrigeration cycle device 200 includes the scroll compressor 100 of the first to eighth embodiments. Therefore, the refrigeration cycle device 200 can exert the same effect as the effect of the scroll compressor 100 described above.
  • valve seat hole 52d is not limited to the fan shape, but may be an elliptical shape, an elongated hole shape, a strip shape, an arc shape, or the like.
  • the shapes of the plurality of valve seat holes 52d may be the same or different.
  • the embodiments of the present disclosure may be used in combination with the configurations of the embodiments 1 to 8.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2020/037421 2020-10-01 2020-10-01 スクロール圧縮機、及び、冷凍サイクル装置 Ceased WO2022070382A1 (ja)

Priority Applications (3)

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JP2022553374A JP7337283B2 (ja) 2020-10-01 2020-10-01 スクロール圧縮機、及び、冷凍サイクル装置
US18/006,194 US12006934B2 (en) 2020-10-01 2020-10-01 Scroll compressor and refrigeration cycle apparatus
PCT/JP2020/037421 WO2022070382A1 (ja) 2020-10-01 2020-10-01 スクロール圧縮機、及び、冷凍サイクル装置

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Cited By (1)

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EP4506566A4 (en) * 2022-05-06 2025-06-04 Mitsubishi Heavy Industries Thermal Systems, Ltd. COMPRESSOR

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DE102024206728A1 (de) * 2024-07-17 2026-01-22 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Scrollmaschine

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JP2001193649A (ja) * 1999-12-28 2001-07-17 Zexel Valeo Climate Control Corp 往復式冷媒圧縮機
JP2004360644A (ja) * 2003-06-06 2004-12-24 Sanden Corp スクロール型流体機械
JP2013072345A (ja) * 2011-09-27 2013-04-22 Toyota Industries Corp 圧縮機
WO2017138131A1 (ja) * 2016-02-10 2017-08-17 三菱電機株式会社 スクロール圧縮機

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JP2003120563A (ja) 2001-10-09 2003-04-23 Seiko Instruments Inc 気体圧縮機
JP5652613B2 (ja) * 2011-03-08 2015-01-14 サンデン株式会社 圧縮機の弁装置
CN209856036U (zh) * 2019-04-26 2019-12-27 艾默生环境优化技术(苏州)有限公司 涡旋压缩机

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JP2001193649A (ja) * 1999-12-28 2001-07-17 Zexel Valeo Climate Control Corp 往復式冷媒圧縮機
JP2004360644A (ja) * 2003-06-06 2004-12-24 Sanden Corp スクロール型流体機械
JP2013072345A (ja) * 2011-09-27 2013-04-22 Toyota Industries Corp 圧縮機
WO2017138131A1 (ja) * 2016-02-10 2017-08-17 三菱電機株式会社 スクロール圧縮機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4506566A4 (en) * 2022-05-06 2025-06-04 Mitsubishi Heavy Industries Thermal Systems, Ltd. COMPRESSOR

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US12006934B2 (en) 2024-06-11
US20230258178A1 (en) 2023-08-17
JPWO2022070382A1 (https=) 2022-04-07

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