WO2023233838A1 - Compresseur et dispositif de cycle de réfrigération - Google Patents

Compresseur et dispositif de cycle de réfrigération Download PDF

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Publication number
WO2023233838A1
WO2023233838A1 PCT/JP2023/015067 JP2023015067W WO2023233838A1 WO 2023233838 A1 WO2023233838 A1 WO 2023233838A1 JP 2023015067 W JP2023015067 W JP 2023015067W WO 2023233838 A1 WO2023233838 A1 WO 2023233838A1
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Prior art keywords
gas
cylinder
compressor
liquid separation
chamber
Prior art date
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PCT/JP2023/015067
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English (en)
Japanese (ja)
Inventor
武士 知念
卓也 平山
雅也 市原
暁地 張
宏 石川
大貴 藤井
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東芝キヤリア株式会社
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Publication of WO2023233838A1 publication Critical patent/WO2023233838A1/fr

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    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • 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
    • F04B39/16—Filtration; Moisture separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation

Definitions

  • Embodiments of the present invention relate to a compressor and a refrigeration cycle device.
  • an accumulator is installed adjacent to the compressor.
  • the refrigerant circulating through the piping is introduced into an accumulator before being sucked into the compressor, and if the refrigerant contains refrigerant in the form of liquid or droplets (referred to as "liquid refrigerant"), this is separated in the accumulator. This prevents liquid refrigerant from being directly sucked into the compressor.
  • Patent Document 1 discloses, as a high-pressure type compressor, a compressor in which a space used for gas-liquid separation of refrigerant is provided in addition to a housing chamber for a motor and a compression mechanism inside a sealed case.
  • the inside of the sealed case is divided by a member called an inner shell into a low-pressure part to which the suction pipe is connected and a high-pressure part to which the discharge pipe is connected.
  • the low pressure section is used for gas-liquid separation of refrigerant, while the rotor of the motor and the compression mechanism section are arranged in the high pressure section. Therefore, the area around the compression chamber becomes a high-pressure atmosphere filled with compressed discharged refrigerant, and the refrigerant in the low-pressure section is susceptible to heat from the discharged refrigerant, causing damage to the compression mechanism, especially the sliding parts of the compression chamber. There is still room for improvement in preventing overheating. Furthermore, there is also a need for further efficiency in the gas-liquid separation of refrigerants.
  • the present invention provides a compressor and refrigeration cycle device that can achieve more efficient arrangement of the compressor, suppress overheating of the compression mechanism, and promote efficient gas-liquid separation of refrigerant.
  • the purpose is to provide.
  • a compressor includes a case, a motor housed in the case, and a compression mechanism housed in the case and configured to be driven by the motor, and includes an interior of the case.
  • a gas-liquid separation chamber is provided, the gas-liquid separation chamber being at least partially defined by the element forming the compression chamber.
  • the gas-liquid separation chamber is provided around the compression chamber, and at least part of it is formed by the elements forming the compression chamber, so that the compressor itself has an accumulator function, and the accumulator can be installed separately. This makes it possible to reduce the space required for compressors and realize a more efficient arrangement of compressors.
  • the compression chamber is cooled by the refrigerant present in the gas-liquid separation chamber, and excessive heat generation occurs in the sliding parts of the compression mechanism, and the It becomes possible to suppress the refrigerant from reaching an overheating state.
  • the heat generated when compressing the refrigerant in other words, the heat transferred from the compression chamber, promotes the vaporization of the liquid refrigerant contained in the refrigerant, thereby reducing the liquid refrigerant itself and sucking the liquid refrigerant into the compression chamber. It becomes possible to suppress the This contributes to efficient gas-liquid separation of the refrigerant.
  • the compressor includes a cylindrical cylinder, a rotor rotatably disposed on the inner diameter side of the cylinder, and a rotor disposed between the cylinder and the rotor so as to be movable in a radial direction with respect to the rotor. It is possible to include a vane that partitions a space between the cylinder and the rotor into a suction chamber and a compression chamber. In this case, the gas-liquid separation chamber is preferably formed outside the compression chamber in the radial direction of the cylinder.
  • the compressor can be suitably implemented by providing a cylinder and a rotor, and partitioning a suction chamber and a compression chamber by vanes.
  • the gas-liquid separation chamber is formed outside the compression chamber in the radial direction of the cylinder, so that the dimensions of the compressor, such as the height when the compressor is installed vertically, can be reduced. It becomes possible to suppress the
  • the gas-liquid separation chamber is formed in an outer peripheral portion of the cylinder outside the compression chamber in the radial direction.
  • the gas-liquid separation chamber is formed in a part of the cylinder, specifically, in the outer periphery of the cylinder on the outside of the compression chamber in the radial direction. It becomes easy to reduce the number of parts, reduce the number of joints with other parts, and ensure the hermeticity of the gas-liquid separation chamber.
  • the compressor further includes a pair of end plate portions disposed in contact with each of both axial ends of the cylinder, each of the end plate portions having a space in which the rotor of the cylinder is accommodated. It is preferable to have an inner diameter portion that closes the gas-liquid separation chamber, and an outer diameter portion that closes the gas-liquid separation chamber.
  • the end plate part that contacts the end in the axial direction of the cylinder is provided, and by closing the gas-liquid separation chamber with the outer diameter part of this end plate part, a separate or It is economical as there is no need to prepare special parts. Furthermore, it is possible to simultaneously finish the inner diameter portion that closes the housing portion of the rotor and the outer diameter portion by a single process including polishing, which is advantageous in terms of workability.
  • the compressor is installed vertically so that the motor is located above the compression mechanism section, communicates the gas-liquid separation chamber with the compression chamber, and removes lubricating oil mixed into the gas-liquid separation chamber.
  • a liquid return passage capable of introducing into the compression chamber, the liquid return passage being formed on a surface of the lower end plate portion that contacts the end surface of the cylinder, or defined by the lower end plate portion. It is preferable to
  • the compressor includes a cylindrical cylinder, a rotor rotatably disposed on the inner diameter side of the cylinder, and a rotor disposed between the cylinder and the rotor so as to be movable in a radial direction with respect to the rotor.
  • a vane that partitions a space between the cylinder and the rotor into a suction chamber and a compression chamber, and the gas-liquid separation chamber may be formed outside the compression chamber with respect to the axial direction of the cylinder. It is possible.
  • the compressor can be suitably implemented by providing a cylinder and a rotor, and partitioning a suction chamber and a compression chamber by vanes.
  • the gas-liquid separation chamber is formed outside the compression chamber in the axial direction of the cylinder, which reduces the dimensions of the compressor, such as the installation area when the compressor is installed vertically. It becomes possible to reduce the
  • the compressor further includes a bearing disposed outside the compression chamber in the axial direction, the bearing having a bearing portion that supports the rotation shaft of the rotor, and the gas-liquid separation chamber comprising: It is preferable to form the bearing part on the outside in the radial direction of the bearing part.
  • the gas-liquid separation chamber is formed outside the bearing part of the bearing in the radial direction. It becomes possible to form a gas-liquid separation chamber while effectively utilizing the space between the compressor and the compressor and suppressing an increase in the installation area of the compressor.
  • the bearing includes an inner diameter portion that supports the rotational shaft of the rotor and is the bearing portion, and an outer diameter portion that is provided concentrically with the inner diameter portion and spaced apart from the inner diameter portion in a radial direction. and a connecting portion connecting the inner diameter portion and the outer diameter portion, and the gas-liquid separation chamber is formed as a space surrounded by the inner diameter portion, the outer diameter portion, and the connecting portion. is preferred.
  • the gas-liquid separation chamber is formed as a space surrounded by the inner diameter part, the outer diameter part, and the connecting part. Therefore, it becomes easy to ensure the sealing property of the gas-liquid separation chamber, especially the sealing property of the compression chamber.
  • the bearing further includes a communication path that allows the gas-liquid separation chamber and the compression chamber to communicate with each other and allows the gas refrigerant present in the gas-liquid separation chamber to be introduced into the compression chamber.
  • the communication passage that communicates the gas-liquid separation chamber and the compression chamber is formed in the bearing, and the gaseous refrigerant present in the gas-liquid separation chamber can be introduced into the compression chamber through this communication passage. There is no need to prepare a special member to form the passage, which is economical.
  • the compressor includes an end plate portion that is disposed in contact with a lower end of the cylinder in the axial direction and closes a space in which the rotor of the cylinder is accommodated from below, and a portion that connects the end plate portion and the cylinder from below. It is preferable to further include a presser bolt that penetrates in the axial direction to reach the bearing and fixes the end plate portion and the cylinder to the bearing by co-tightening.
  • the cylinder and the end plate disposed below are fixed together by the presser bolt that passes through the cylinder and the end plate from below in the axial direction and reaches the bearing, so that the fastener This prevents the sealing performance of the gas-liquid separation chamber from being compromised due to the use of the bearing, and also suppresses the effect of this liquid refrigerant on the bolt axial force when liquid refrigerant gets mixed into the gas-liquid separation chamber formed in the bearing. becomes possible.
  • a refrigeration cycle device includes the compressor, a condenser, an expansion valve, and an evaporator, and includes the compressor, the condenser, the expansion valve, and the evaporator. are connected by a refrigerant pipe, and the refrigerant discharged from the compressor is circulated through the refrigerant pipe to the condenser, the expansion valve, and the evaporator.
  • a compressor and a refrigeration cycle device are capable of realizing a more efficient arrangement of the compressor, suppressing overheating of the compression mechanism, and promoting efficient gas-liquid separation of refrigerant. can be provided.
  • FIG. 1 is a schematic diagram showing the overall configuration of a refrigeration cycle device according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view taken along a plane including the central axis of the sealed case, showing the internal configuration of the compressor according to the embodiment.
  • 3 is a cross-sectional view taken along line AA shown in FIG. 2.
  • FIG. 3 is a cross-sectional view taken along a plane including the central axis of a sealed case, showing the internal configuration of a compressor according to another embodiment of the present invention.
  • FIG. 5 is a cross-sectional view taken along a plane different from FIG. 4 and including the central axis of the sealed case, showing the internal configuration of the compressor according to the embodiment.
  • FIG. 1 is a schematic diagram showing the overall configuration of a refrigeration cycle device U according to an embodiment of the present invention.
  • the refrigeration cycle device U is a heat pump type refrigeration cycle device.
  • the refrigeration cycle device U can be applied to an air conditioner, a refrigerator, a refrigerator, a water heater, etc., and can also be used with a cooling/heating device or a hot water storage device (not shown) configured as an external device. It is also possible to apply it to a heat source unit that cools or heats a circulating fluid. Although water is generally used as the fluid to be used, brine can also be used for purposes such as anti-freezing.
  • the refrigerant circulated through the refrigeration cycle device U is, for example, an HFC refrigerant such as R410A or R32, an HFO refrigerant such as R1234yf, or a natural refrigerant such as carbon dioxide (CO 2 ) or propane.
  • the refrigeration cycle device U includes a compressor 1A, a first heat exchanger 2, a second heat exchanger 3, a four-way valve 4, and an expansion valve 5 as main components, and fluidly connects these components.
  • a refrigerant pipe 6 is provided for circulating refrigerant between these components.
  • the refrigerant circulates while changing its phase between a gas refrigerant and a liquid refrigerant.
  • the compressor 1A is a so-called high-pressure type compressor, and in this embodiment, it is a rotary compressor. As will be explained in more detail later, the compressor 1A includes a high-pressure sealed case 11 as its outer shell, and a motor 12 and a rotary compression mechanism section 13 using the motor 12 as a drive source are housed inside the case 11. .
  • the compressor 1A may be capable of changing its operating frequency through known inverter control, or may be operated at a constant speed using a commercial frequency.
  • the first heat exchanger 2 is installed outdoors and exchanges heat between the outside air and the refrigerant.
  • the first heat exchanger 2 is housed in a case of the outdoor unit together with an outdoor blower (not shown) as a component of the outdoor unit.
  • a fin-and-tube type heat exchanger can be exemplified as one applicable to the first heat exchanger 2.
  • the second heat exchanger 3 is installed indoors and performs heat exchange between the indoor air, which is the fluid to be adjusted, and the refrigerant.
  • the second heat exchanger 3 is housed in a case of the indoor unit together with an indoor blower (not shown) as a component of the indoor unit.
  • an indoor blower not shown
  • a fin-and-tube type heat exchanger can be used as an example of the second heat exchanger 3.
  • the four-way valve 4 switches the flow path of the refrigerant discharged by the compressor 1A between the cooling operation (cooling time) and the heating operation (heating time) of the air conditioner.
  • the four-way valve 4 sets the refrigerant flow path in the direction from the four-way valve 4 toward the first heat exchanger 2 .
  • the refrigerant that has exited the four-way valve 4 passes through the first heat exchanger 2 and then flows into the second heat exchanger 3.
  • the refrigerant flow path is switched from the four-way valve 4 to the second heat exchanger 3.
  • the refrigerant that has exited the four-way valve 4 passes through the second heat exchanger 3 and then flows into the first heat exchanger 2.
  • the first heat exchanger 2 operates as a condenser during cooling and as an evaporator during heating
  • the second heat exchanger 3 operates as an evaporator during cooling and as a condenser during heating.
  • the condenser the high-temperature, high-pressure gas refrigerant sent from the compressor 1A is changed into high-pressure liquid refrigerant through heat exchange, and in the evaporator, the low-temperature, low-pressure liquid refrigerant sent from the expansion valve 5, which will be described next, is converted into a low-pressure liquid refrigerant. Changes to gaseous refrigerant.
  • the expansion valve 5 adjusts the pressure of the refrigerant exiting the condenser (specifically, the first or second heat exchanger 2, 3 that operates as a condenser) by the action of an orifice, and adjusts the flow rate. By creating a pressure drop due to the resistance, the pressure of the refrigerant heading toward the evaporator (specifically, the second or first heat exchanger 3, 2 that operates as an evaporator) is adjusted.
  • the expansion valve 5 for example, a stepping motor-driven electronic expansion valve can be used. In the process of adjusting the pressure by the expansion valve 5, the high-pressure liquid refrigerant sent from the condenser changes to low-temperature, low-pressure liquid refrigerant.
  • the refrigerant pipe 6 connects the compressor 1A, the first heat exchanger 2, the second heat exchanger 3, the four-way valve 4, and the expansion valve 5 so that the refrigerant can flow therebetween.
  • the refrigerant pipe 6 can be roughly divided into a first refrigerant pipe 6a connected to the compressor 1A and the four-way valve 4, and a second refrigerant pipe 6a connected to the four-way valve 4 and the first heat exchanger 2.
  • the four-way valve 4 connects the inlet 4a and the first outlet 4b, and also connects the second outlet 4c and the outlet 4d.
  • the refrigerant discharged from the compressor 1A heads to the first heat exchanger 2 via the four-way valve 4, receives the action of the expansion valve 5, passes through the second heat exchanger 3, and passes through the four-way valve 4. 4 and returns to the compressor 1A.
  • the four-way valve 4 switches the connection destination of the inflow port 4a to the second outflow port 4c, and switches the connection destination of the outflow port 4d to the first outflow port 4b.
  • the refrigerant discharged from the compressor 1A heads to the second heat exchanger 3 via the four-way valve 4, receives the action of the expansion valve 5, passes through the first heat exchanger 2, and then passes through the four-way valve 4. 4 and returns to the compressor 1A.
  • FIG. 2 is a sectional view taken along a plane including the central axis Ax1 of the sealed case (hereinafter simply referred to as "case") 11, showing the internal configuration of the compressor 1A according to the present embodiment
  • FIG. 3 is a cross-sectional view taken along line AA.
  • the compressor 1A includes a case 11, a motor 12, and a compression mechanism section 13.
  • the case 11 includes a case main body 11a, a case upper part 11b, and a case bottom part 11c.
  • the case main body 11a has an open upper end, a lower end formed integrally with the case bottom 11c, and has a space S therein for accommodating the motor 12 and the compression mechanism section 13.
  • the case upper part 11b is joined to the upper end of the case main body 11a, and airtightly closes the opening at the upper end of the case main body 11a.
  • the case body 11a and the case bottom 11c are integrally formed into a cylindrical shape with a bottom, but the case body 11a and the case bottom 11c are formed separately and penetrate through the case 11 vertically.
  • case bottom 11c is joined to the lower end of the case main body 11a, and airtightly closes the opening at the lower end of the case main body 11a.
  • the case upper part 11b is formed of a dish-shaped end plate, and is respectively joined to the case main body 11a by an appropriate method such as welding.
  • the compressor 1A is installed vertically so that the central axis Ax1 of the case 11 is vertical, that is, the motor 12 and the compression mechanism section 13 are vertically overlapped inside the case 11.
  • the motor 12 is housed inside the case 11 in the upper half of the case body 11a.
  • the compression mechanism section 13 is housed inside the case 11 in the lower half of the case body 11a.
  • the motor 12 constitutes a drive source for the compression mechanism section 13 and includes a stator 121 and a rotor 122.
  • the stator 121 has a cylindrical shape and is fixed to the case body 11a, and the rotor 122 is disposed on the inner diameter side of the stator 121 and is rotatably supported by the case body 11a.
  • a rotor 122 is connected to the compression mechanism section 13 via a rotating shaft 14, and an electromagnetic attraction force is exerted on the rotor 122 by energizing an electromagnetic coil 121a formed on the stator 121, so that the rotor Rotate 122. Then, the motor 12 transmits the driving force in the rotational direction generated in the rotor 122 to the compression mechanism section 13 via the rotating shaft 14, and drives the compression mechanism section 13.
  • the terminal section 15 connects a lead wire (also referred to as a "power line”), which is not shown outside the case 11, extending from the power source of the motor 12 (for example, a commercial AC power source) or a power converter such as an inverter, from the coil winding of the electromagnetic coil 121a.
  • a lead wire also called an "output wire”
  • the terminal section 15 includes an installation stand 151 and a plurality of terminal pins 152.
  • the installation stand 151 is fitted into an insertion opening formed in the case upper part 11b and is fixed to the case upper part 11b.
  • the terminal pin 152 is a flat tab terminal fixed to the terminal pin 152, and is attached to the installation base 151 so as to pass through the front and back sides of the installation base 151.
  • the installation stand 151 ensures an insulating distance between the terminal pins 152.
  • the compression mechanism section 13 operates using the motor 12 as a drive source, compresses the refrigerant sucked in from the suction pipe 1a (hereinafter sometimes referred to as “suction refrigerant”), and compresses the refrigerant (hereinafter sometimes referred to as “discharge refrigerant”). ) is discharged through the discharge pipe 1b.
  • the compressor 1A is a sliding vane type compressor, and the compression mechanism section 13 is roughly divided into a cylinder 131, a rotor 132, a vane 133, a main bearing 134, and a sub-bearing 135. , and a discharge muffler 136.
  • the cylinder 131 has a cylindrical shape as a whole, and is fixed coaxially with the rotor 122 of the motor 12 and the rotating shaft 14 with respect to the case body 11a.
  • the cylinder 131 has a housing chamber for the rotor 132 in its inner diameter portion, and a discharge chamber Cd on the outside in the radial direction with respect to the housing chamber for the rotor 132.
  • the housing chamber of the rotor 132 is connected to the suction pipe 1a and the discharge chamber Cd via a suction port h1 and a discharge port h2 formed in the inner wall of the cylinder 131, respectively.
  • the housing chamber of the rotor 132 has a substantially circular shape and is eccentrically formed with respect to the central axis of the cylinder 131 (that is, the rotating shaft 14).
  • the rotor 132 is housed on the inner diameter side of the cylinder 131 and is rotatably connected to the rotor 122 of the motor 12 via the rotating shaft 14.
  • the rotor 132 and the rotating shaft 14 are concentric with each other and are rotatably supported by the cylinder 131.
  • the rotor 132 is formed with a plurality of grooves g that extend radially outward and open on the outer circumferential surface of the rotor 132, and a vane 133 is housed in each of the plurality of grooves g.
  • the vanes 133 are pressed against the inner circumferential surface of the cylinder 131 by back pressure and come into sliding contact, thereby dividing the space between the cylinder 131 and the rotor 132 into a suction chamber Ci and a compression chamber Cc. There is an interval between.
  • the suction chamber Ci communicates with the suction port h1
  • the compression chamber Cc communicates with the discharge port h2.
  • the compression mechanism section 13 sucks in refrigerant and compresses it as the rotor 132 rotates inside the cylinder 131 .
  • the cylinder 131 has a shape in which a part of the outer periphery is cut along a chord connecting two points on the outer periphery, and a discharge chamber Cd that opens at the cut surface is formed. It has a sealing plate 131a joined to the surface so as to close the discharge chamber Cd.
  • the cylinder 131 further has a discharge valve 131b that closes the discharge port h2, and when the refrigerant inside the compression chamber Cc reaches the valve opening pressure of the discharge valve 131b, the discharge valve 131b is opened and the refrigerant is discharged from the discharge port h2. It flows out into chamber Cd.
  • the main bearing 134 is arranged between the motor 12 and the compression mechanism section 13 and supports the rotating shaft 14.
  • the sub bearing 135 is arranged on the opposite side of the main bearing 134 with respect to the compression mechanism section 13, and supports the rotating shaft 14 together with the main bearing 134.
  • the discharge muffler 136 is arranged concentrically with the main bearing 134 and forms a muffler chamber between it and the main bearing 134.
  • the refrigerant discharged from the compression chamber Cc to the discharge chamber Cd flows into the discharge muffler 136 via the communication passage p2 formed through the cylinder 131 and the main bearing 134, and flows to the inner diameter side of the discharge muffler 136. , flows into the case 11 through an annular communication port h3 formed between the main bearing 134 and the main bearing 134.
  • the refrigerant reaches the discharge pipe 1b through the gap between the stator 121 of the motor 12 and the inner circumferential surface of the case 11, a communication passage (not shown) formed in the rotor 122, etc., and then flows through the discharge pipe 1b. It flows out from the compressor 1A.
  • lubricating oil is sealed in the lower half of the case body 11a and the case bottom 11c, and the compression mechanism section 13 is immersed in this lubricating oil.
  • the compressor 1A has a gas-liquid separation chamber Cb inside the case 11.
  • the gas-liquid separation chamber Cb is provided around the compression chamber Cc of the compression mechanism section 13, and is at least partially defined by elements forming the compression chamber Cc.
  • the elements forming the compression chamber Cc are, for example, the cylinder 131, the rotor 132, the main bearing 134, and the sub-bearing 135. In this embodiment, the cylinder 131, the main bearing 134, and the sub-bearing 135 are employed.
  • the gas-liquid separation chamber Cb also called a buffer chamber, is located between the suction pipe 1a and the suction port h1, receives refrigerant from the suction pipe 1a, and separates liquid refrigerant when the refrigerant contains liquid refrigerant. do.
  • the gas-liquid separation chamber Cb is formed outside the compression chamber Cc in the radial direction of the cylinder 131, and specifically, the gas-liquid separation chamber Cb is formed outside the compression chamber Cc in the radial direction of the cylinder 131. It is formed on the outer periphery of the That is, in this embodiment, the gas-liquid separation chamber Cb is formed in the cylinder 131 itself, and in the cross section shown in FIG. The cylinder 131 is isolated from the space outside the cylinder 131 by its peripheral edge. Furthermore, the gas-liquid separation chamber Cb is formed in the circumferential direction centered on the central axis Ax1 of the case 11 over the entire outer circumference excluding the discharge chamber Cd.
  • the end plate part 134a of the main bearing 134 and the end plate part 135a of the sub-bearing 135 are each extended radially outward to the peripheral edge of the cylinder 131, and the main bearing 134
  • the end plate portion 134 a of the cylinder 131 is in contact with one shaft end surface of the cylinder 131 and closes the storage chamber of the rotor 132 and the gas-liquid separation chamber Cb.
  • the housing chamber of the rotor 132 is closed, and the gas-liquid separation chamber Cb is closed.
  • the "end plate part” is a disc-shaped part extending radially outward from the cylindrical bearing part that faces and supports the rotating shaft 14. Part.
  • the end plate portion 134a of the main bearing 134 and the end plate portion 135a of the sub-bearing 135 each have an inner peripheral portion that closes the accommodation chamber of the rotor 132 and an outer peripheral portion that closes the gas-liquid separation chamber Cb. .
  • a liquid return passage p1 is formed in an end plate portion 135a in contact with the lower shaft end surface of the cylinder 131 so as to straddle the inner wall portion of the cylinder 131 that defines the suction chamber Ci.
  • the liquid return passage p1 is in the form of a groove bored in the joint surface of the end plate portion 135a, and communicates the bottoms of the gas-liquid separation chamber Cb and the compression chamber Cc, so that the gas-liquid separation The lubricating oil mixed into the chamber Cb can be introduced into the compression chamber Cc.
  • the liquid return passage p1 can be formed not only as a groove but also as a hole.
  • a hole is formed in the inner wall of the cylinder 131 that separates the gas-liquid separation chamber Cb and the compression chamber Cc, and the gas-liquid separation chamber Cb and the compression chamber Cc are communicated through this hole. It is.
  • the refrigeration cycle device U and compressor 1A according to this embodiment have the above configurations, and the effects obtained by this embodiment will be described below.
  • the compressor 1A itself has the function of an accumulator, which is generally placed outside the sealed case, and the gas-liquid separation chamber Cb is placed inside the case 11, specifically, the compression chamber Cc.
  • the compressor By forming the compressor around the accumulator, it is possible to reduce the space required when installing the accumulators individually, and to arrange the compressor 1A more efficiently.
  • the refrigerant present in the gas-liquid separation chamber Cb cools the compression chamber Cc, especially the sliding parts such as the tips of the vanes 133.
  • the refrigerant it is possible to avoid a situation in which excessive heat generation occurs in the sliding portion or the compressed refrigerant reaches an overheated state.
  • the heat generated during compression in other words, the heat transmitted from the compression chamber Cc, is used to promote the vaporization of the liquid refrigerant contained in the refrigerant, reducing the amount of liquid refrigerant itself, promoting gas-liquid separation, and It is possible to suppress suction of liquid refrigerant into Cc.
  • the amount of refrigerant supplied to the compression chamber Cc is ensured, and the liquid refrigerant is sucked into the compression chamber Cc, or a shortage occurs in the amount of refrigerant sucked into the compression chamber Cc. This makes it possible to suppress problems caused by this.
  • the gas-liquid separation chamber Cb is provided around the compression chamber Cc, and the gas-liquid separation chamber Cb and the compression chamber Cc are located close to each other, thereby promoting active use of heat generated during compression. becomes possible.
  • the dimensions of the compressor 1A for example, the height when the compressor 1A is placed vertically, can be reduced. It becomes possible to suppress this.
  • the gas-liquid separation chamber Cb is located on the outer periphery of the cylinder 131, the compression chamber Cc formed on the inner diameter side of the cylinder 131, especially in the sliding vane type compressor 1A, the cylinder 131 has a large influence of friction. It becomes possible to effectively cool the sliding portion between the inner peripheral portion and the vane 133.
  • the lubricating oil mixed into the gas-liquid separation chamber Cb is introduced into the compression chamber Cc via the liquid return passage p1, and the lubricating oil is accumulated in the gas-liquid separation chamber Cb, which substantially contributes to the gas-liquid separation of the refrigerant. This makes it possible to prevent situations in which there is a shortage of space that contributes to this.
  • the liquid return passage p1 in the lower end plate part 135a or defining it by the lower end plate part 135a, when the compressor 1A is arranged vertically, the liquid return passage p1 can be connected to the liquid return passage p1. It becomes possible to encourage the inflow of lubricating oil by gravity.
  • FIG. 4 is a sectional view taken along a plane including the central axis Ax1 of the sealed case 11, showing the internal structure of a compressor 1B according to another embodiment of the present invention
  • FIG. 5 shows the internal structure of the compressor 1B.
  • FIGS. 4 and 5 elements corresponding to those of the compressor 1A according to the previous embodiment are given the same reference numerals as shown in FIG. 2, and repeated explanations thereof will be omitted.
  • the compressor 1B according to this embodiment can be applied to a refrigeration cycle device U having a configuration similar to that shown in FIG.
  • FIG. 6 is a partial cross-sectional view showing the configuration of the main bearing 137 of the compression mechanism section 13 and its surroundings in the compressor 1B according to the present embodiment.
  • the compressor 1B according to this embodiment will be explained with reference to FIG. 6 as appropriate, focusing on the differences from the compressor 1A according to the previous embodiment.
  • the compressor 1B differs from the compressor 1A according to the previous embodiment mainly in the configuration related to the gas-liquid separation chamber Cb.
  • the gas-liquid separation chamber Cb is provided around the compression chamber Cc of the compression mechanism section 13, and is at least partially defined by elements forming the compression chamber Cc.
  • the gas-liquid separation chamber Cb is formed outside the compression chamber Cc in the axial direction of the cylinder 131 and radially outside the bearing portion of the main bearing 137 that supports the rotating shaft 14 of the rotor 132. has been done.
  • the main bearing 137 includes an inner diameter portion 137a that supports the rotating shaft 14, an outer diameter portion 137b that is provided concentrically with respect to the inner diameter portion 137a and spaced apart from the inner diameter portion 137a in the radial direction, and an inner diameter portion.
  • 137a and the outer diameter part 137b, and the gas-liquid separation chamber Cb is formed as a space surrounded by the inner diameter part 137a, the outer diameter part 137b, and the coupling part 137c. There is.
  • the gas-liquid separation chamber Cb is in a state in which the radial inner side, radial outer side, and lower side are shielded by these elements 137a, 137b, and 137c of the main bearing 137, and the inner diameter portion 137a is shielded from the entire circumference. It is formed so as to surround the area.
  • the inner diameter portion 137a corresponds to a bearing portion of the main bearing 137
  • the connecting portion 137c functions as an end plate portion that is in contact with one shaft end surface of the cylinder 131 and closes the accommodation chamber of the rotor 132. be. That is, in this embodiment, the housing chamber of the rotor 132 is sealed in the axial direction by the connecting portion 137c of the main bearing 137 and the end plate portion 135a of the sub-bearing 135.
  • the main bearing 137 is configured to have an opening provided in the outer diameter portion 137b, and to receive the refrigerant from the suction pipe 1a into the gas-liquid separation chamber Cb by connecting the suction pipe 1a to this opening. .
  • An end plate material 138 is attached to the upwardly opening shaft end surface of the main bearing 137, and the gas-liquid separation chamber Cb is closed by this end plate material 138 from above.
  • a communication passage p3 that communicates the gas-liquid separation chamber Cb and the suction port h1 is formed in the outer diameter portion 137b of the main bearing 137, and the main bearing defining the communication passage p3
  • a communication port h4 is formed in the inner wall of 137, passing through the inner wall and communicating the gas-liquid separation chamber Cb with the communication path p3.
  • the communication path p3 is formed as a cylindrical space extending in a direction parallel to the axial direction of the cylinder 131, terminates near the shaft end of the main bearing 137, and has a slight gap g1 between it and the end plate material 138. form.
  • the opening area of this gap g1 makes it possible to adjust the flow resistance or fluid loss of the refrigerant from the gas-liquid separation chamber Cb to the suction port h1.
  • the refrigerant that has flowed into the communication path p3 from the gas-liquid separation chamber Cb is introduced into the suction chamber Cs, and is transferred from the suction chamber Cs to the cylinder 131 and the rotor 131 through the suction port h1. is inhaled into the suction chamber Ci between the In FIG.
  • the flow of refrigerant flowing from the suction pipe 1a to the gas-liquid separation chamber Cb is indicated by an arrow a1
  • the flow of the refrigerant flowing from the gas-liquid separation chamber Cb to the communication passage p3 is indicated by an arrow a2
  • the flow of the refrigerant flowing from the communication passage p3 to the communication passage p3 is indicated by an arrow a2.
  • the flow of refrigerant flowing into the suction chamber Cs is indicated by an arrow a3
  • the flow of refrigerant flowing into the suction chamber Ci from the suction chamber Cs via the suction port h1 is indicated by an arrow a4.
  • the communication port h4 forms a liquid return passage, and allows the liquid refrigerant after gas-liquid separation and the lubricating oil mixed in the gas-liquid separation chamber Cb to escape to the communication passage p3 and be introduced into the compression chamber Cc.
  • arrows a5 indicate the flow of liquid refrigerant and lubricating oil flowing from the gas-liquid separation chamber Cb into the communication path p3 via the communication port h4.
  • FIG. 9 is a partial cross-sectional view showing the support structure of the compression mechanism section 13 in the compressor 1B according to the present embodiment.
  • a presser bolt 140 is employed as a fastener for the compression mechanism section 13. Specifically, a through hole is formed that penetrates both the cylinder 131 and the end plate portion 135a of the sub-bearing 135 from below and reaches the connecting portion 137c of the main bearing 137, and a through hole is formed on the inner periphery of the hole of the connecting portion 137c. Form a female thread. Then, the holding bolt 140 is inserted from below into the end plate portion 135a and the cylinder 131 in this order, and is screwed into the female thread of the connecting portion 137c. In this way, the cylinder 131 and the sub-bearing 135 are fastened together to the main bearing 137 and fixed. By fixing the main bearing 137 to the case 11, it is possible to fix the entire compression mechanism section 13 to the case 11.
  • the rotating shaft 14 Although it may involve an extension of the length dimension, the space between the motor 12 and the compression mechanism section 13 can be used effectively, and the gas-liquid separation chamber Cb can be expanded without increasing the installation area of the compressor 1B. It becomes possible to form. In other words, it becomes easy to secure a space for forming the gas-liquid separation chamber Cb.
  • the air By forming the inner diameter part 137a, the outer diameter part 137b, and the connecting part 137c in the main bearing 137, and forming the gas-liquid separation chamber Cb as a space surrounded by the inner diameter part 137a, the outer diameter part 137b, and the connecting part 137c, the air
  • the sealing property of the liquid separation chamber Cb, especially the sealing property with respect to the compression chamber Cc, can be easily ensured.
  • the refrigerant present in the gas-liquid separation chamber Cb can be introduced into the compression chamber Cc via the communication path p3.
  • the communication passage p3 in the main bearing 137 specifically, the outer diameter portion 137b thereof, there is no need to prepare a special member for forming the communication passage p3, which is economical as well. , it becomes possible to ensure resistance to thermal shock when liquid refrigerant is mixed into the gas-liquid separation chamber Cb.
  • the communication path p3 of the main bearing 137 that connects the gas-liquid separation chamber Cb and the suction port h1 is formed by the inner wall of the main bearing 137 (FIG. 6).
  • the communication path p3 is not limited to this, and may be formed using a dedicated member.
  • FIG. 7 is a partial sectional view showing the configuration of the main bearing 137 of the compression mechanism section 13 and its surroundings in a compressor according to a first modification of the present embodiment.
  • a cylindrical member 139 that is separate from the main bearing 137 is employed and is embedded in the outer diameter portion 137b of the main bearing 137 to form the communication path p3.
  • the cylindrical member 139 terminates near the shaft end of the main bearing 137, and forms a small gap g2 with the end plate member 138.
  • a hole h5 is formed in the tube wall portion of the cylindrical member 139 to pass through it in the radial direction, so that the gas-liquid separation chamber Cb and the inside of the cylindrical member 139, that is, the communication path p3 are communicated with each other. That is, the through hole h5 replaces the communication port h4 in the previous example and forms a liquid return passage.
  • arrows a6 indicate the flow of liquid refrigerant and lubricating oil flowing from the gas-liquid separation chamber Cb into the communication path p3 via the through hole h5.
  • other arrows a1 to a4 indicate the same flow as in FIG.
  • the communication passage p3 as a separate member from the main bearing 137, it becomes possible to change the dimensions of the communication passage p3 as appropriate depending on the flow rate of the refrigerant, the required storage amount of liquid refrigerant, etc. .
  • the cylindrical member 139 it is possible to optimize or minimize the fluid loss in the communication path p3, thereby minimizing the adverse effects that the formation of the gas-liquid separation chamber Cb has on the operating performance of the compressor. .
  • liquid return passage can be formed not only in the inner wall portion of the main bearing 137 that forms the communication passage p3 or in a separate member, but also in the connecting portion 137c or the end plate portion.
  • FIG. 8 is a partial sectional view showing the configuration of the main bearing 137 of the compression mechanism section 13 and its surroundings in a compressor according to a second modification of the present embodiment.
  • a hole p4 that vertically penetrates the connecting portion 137c of the main bearing 137 is formed as a liquid return passage, and the gas-liquid separation chamber Cb and the suction port h1 or the suction chamber Cs are connected through the through hole p4. to communicate.
  • the negative pressure generated in the suction chamber Ci can be more directly transmitted.
  • the lubricating oil and liquid refrigerant accumulated in the gas-liquid separation chamber Cb can be more actively discharged from the gas-liquid separation chamber Cb.
  • the flow of lubricating oil and liquid refrigerant flowing from the gas-liquid separation chamber Cb into the suction chamber Cs via the through hole p4 is indicated by an arrow a7.
  • sliding vane type compressors are used as the compressors 1A and 1B, but the compressors that can be adopted are not limited to this, and a rolling piston type compressor may also be used. .
  • U... Refrigeration cycle device 1A, 1B... Compressor, 1a... Suction pipe, 1b... Discharge pipe, 11... Sealed case, 12... Motor, 121... Stator, 122... Rotor, 13... Compression mechanism section, 131... Cylinder, 132... Rotor, 133... Vane, 134... Main bearing, 135... Sub bearing, 136... Discharge muffler, 14... Rotating shaft, 2... First heat exchanger, 3... Second heat exchanger, 4... Four-way valve , 5... expansion valve, 6 (6a to 6f)... refrigerant piping, h1... suction port, h2... discharge port, Ci... suction chamber, Cc... compression chamber, Cb... gas-liquid separation chamber, S... space inside the case.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

La présente invention concerne un compresseur (1A) qui comprend : un boîtier (11) ; un moteur (12) logé dans le boîtier ; et une unité de mécanisme de compression (13) logée dans le boîtier et conçue pour pouvoir être entraînée par le moteur. L'intérieur du boîtier est sous une atmosphère à haute pression remplie d'un fluide frigorigène après compression par l'unité de mécanisme de compression (13). L'unité de mécanisme de compression (13) présente, autour d'une chambre de compression (Cc), une chambre de séparation gaz-liquide (Cb) pour séparer le fluide frigorigène aspiré dans la chambre de compression en un fluide frigorigène gazeux et un fluide frigorigène liquide. La chambre de séparation gaz-liquide (Cb) est au moins partiellement délimitée par un élément formant la chambre de compression (Cc).
PCT/JP2023/015067 2022-05-31 2023-04-13 Compresseur et dispositif de cycle de réfrigération WO2023233838A1 (fr)

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JP2022088869 2022-05-31
JP2022-088869 2022-05-31

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS463641Y1 (fr) * 1970-06-25 1971-02-08
JPS50105616U (fr) * 1974-02-04 1975-08-30
JPS53130511A (en) * 1977-04-19 1978-11-14 Matsushita Electric Ind Co Ltd Refrigerant compressor
JPH07310689A (ja) * 1994-05-17 1995-11-28 Matsushita Refrig Co Ltd 回転式圧縮機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS463641Y1 (fr) * 1970-06-25 1971-02-08
JPS50105616U (fr) * 1974-02-04 1975-08-30
JPS53130511A (en) * 1977-04-19 1978-11-14 Matsushita Electric Ind Co Ltd Refrigerant compressor
JPH07310689A (ja) * 1994-05-17 1995-11-28 Matsushita Refrig Co Ltd 回転式圧縮機

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