WO2016189598A1 - Compresseur à volutes - Google Patents

Compresseur à volutes Download PDF

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Publication number
WO2016189598A1
WO2016189598A1 PCT/JP2015/064803 JP2015064803W WO2016189598A1 WO 2016189598 A1 WO2016189598 A1 WO 2016189598A1 JP 2015064803 W JP2015064803 W JP 2015064803W WO 2016189598 A1 WO2016189598 A1 WO 2016189598A1
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WO
WIPO (PCT)
Prior art keywords
scroll
pressure
chamber
space
compression
Prior art date
Application number
PCT/JP2015/064803
Other languages
English (en)
Japanese (ja)
Inventor
令 三坂
茗ヶ原　将史
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2015/064803 priority Critical patent/WO2016189598A1/fr
Priority to JP2017520076A priority patent/JP6395929B2/ja
Priority to CN201610258465.6A priority patent/CN106168212B/zh
Priority to CN201620350387.8U priority patent/CN205638916U/zh
Publication of WO2016189598A1 publication Critical patent/WO2016189598A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—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
    • 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
    • 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
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C29/023—Lubricant distribution through a hollow driving shaft
    • 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

Definitions

  • the present invention relates to a scroll compressor used for applications such as air conditioning and hot water supply.
  • a conventional general scroll compressor includes a compression mechanism section, an electric motor that drives the compression mechanism section, and a main shaft that transmits the rotational force of the electric motor to the compression mechanism section in an airtight container.
  • the compression mechanism portion includes a fixed scroll and a swing scroll having plate-like spiral teeth on the base plate portion, a fixed frame provided with a stationary base, and an Oldham mechanism that prevents the swing scroll from rotating.
  • the fixed scroll and the orbiting scroll are combined so as to mesh with each other's plate-like spiral teeth to form a plurality of compression chambers for compressing the refrigerant gas.
  • the oscillating scroll is held by a fixed scroll and a fixed frame fixed to the hermetic container, and the fixed frame supports the oscillating shaft portion of the main shaft via an oscillating bearing, and the oscillating scroll is rotated by the rotation of the main shaft. Oscillates.
  • an oil sump for storing refrigerating machine oil is the bottom of the sealed container
  • the oil sump is at a high pressure (discharge pressure).
  • a differential pressure oil supply system as an oil supply system for supplying high-pressure refrigerating machine oil to a compression mechanism section located in the upper part of the sealed container.
  • a space having a lower pressure than the discharge pressure (for example, the outer space of the orbiting scroll boss portion) is formed in the vicinity of the compression mechanism portion of the main shaft, and oil is supplied by a differential pressure with respect to a high-pressure oil sump.
  • the refrigerating machine oil in the oil sump rises due to the differential pressure mainly in the oil supply path formed penetrating in the axial direction of the main shaft, and the oscillating scroll boss part from the upper end opening of the oil supply path It flows out into the internal space (hereinafter referred to as the boss portion internal space) and then supplied to the swing scroll boss portion external space (hereinafter referred to as the boss portion external space).
  • a wiring mistake (a wiring mistake to the terminal of the unit (so-called reverse phase in which the order of the phases of the three-phase power supply is shifted)) may occur during installation of the unit (for example, an air conditioner).
  • the reverse phase prevention relay normally operates during driving and power is not supplied to the scroll compressor, but the reverse phase prevention relay is short-circuited or removed to forcibly start the scroll compressor.
  • the scroll compressor performs reverse rotation opposite to normal rotation, that is, reverse rotation operation.
  • the compression mechanism unit When the electric motor of the scroll compressor continuously performs reverse rotation operation, the compression mechanism unit operates as an expander that expands the refrigerant, not a compressor that compresses the refrigerant.
  • the compression mechanism section does not perform the compression operation, so that when the compression operation is performed, the high-pressure gas that should be discharged from the compression chamber into the sealed container is not discharged into the sealed container.
  • the pressure in the sealed container does not increase.
  • hub part exterior space and the inside of an airtight container does not generate
  • a scroll compressor adopting a differential pressure oil supply system, which is sucked from the refrigerant suction port between the refrigerant suction port communicating with the compression chamber of the fixed scroll and the suction pressure space communicating with the suction pipe in the sealed container.
  • a scroll compressor provided with a suction check valve mechanism that prevents a refrigerant from flowing back into the pressure space (see, for example, Patent Documents 1 and 2).
  • this type of scroll compressor when it becomes an expander during reverse rotation operation, the pressure is reduced from the innermost part (innermost chamber) of the compression chamber toward the outermost part (outermost chamber) in the compression mechanism section.
  • the refrigerant reaching the outermost chamber is closed by the suction check valve mechanism, so that the pressure in the outermost chamber rises, while the compression chamber just before the outermost chamber is compared with the innermost chamber. Pressure drops.
  • an intermediate pressure chamber (a chamber formed between the outermost (outermost chamber) of the compression chamber and the innermost chamber) in which the pressure is reduced as compared with the innermost chamber as described above. And a path for communicating with the external space of the boss part.
  • the boss portion outer space is made a low pressure space lower than the pressure inside the sealed container by guiding the pressure from the boss portion outer space to the intermediate pressure chamber through this path, and the low pressure space and the sealed container are This makes it possible to refuel.
  • a through hole is provided in the center of the base plate of the orbiting scroll.
  • the through hole allows refrigerant gas to flow from the inner space of the boss portion of the orbiting scroll to the innermost chamber of the compression chamber.
  • a compressor provided with a check valve mechanism that prevents a flow from the chamber to the internal space of the boss part (see, for example, Patent Document 3).
  • Patent Document 3 when the innermost chamber becomes negative pressure due to the reverse rotation operation of the electric motor, the refrigerant is supplied from the inner space of the boss portion to the innermost chamber via the check valve mechanism. Thus, the negative pressure in the innermost chamber is released, and abnormal wear and damage due to the swinging scroll being pressed against the fixed scroll are prevented.
  • Patent Document 1 and Patent Document 2 a pressure difference between the outer space of the boss part and the inside of the sealed container is made to communicate with the outer space of the boss part by communicating with the intermediate chamber whose pressure is lower than that of the innermost chamber.
  • the oil is supplied to the compression mechanism during reverse operation.
  • a discharge valve mechanism is provided at the discharge port formed in the center of the fixed scroll, and the sealed container is opened from the innermost chamber (compression chamber) through the discharge port. Since it is configured to allow the flow of the refrigerant gas only in one direction to the internal space, there are the following problems. That is, during the reverse rotation operation, the flow of the refrigerant from the sealed container to the innermost chamber is blocked by the discharge valve mechanism, and the refrigerant cannot flow into the innermost chamber from the discharge port. Therefore, the innermost chamber falls into a state close to a vacuum, and the fixed scroll and the orbiting scroll are operated in a pressure contact state, and abnormal wear or the like occurs in the plate-like spiral teeth, resulting in a problem of reducing reliability. .
  • Patent Document 3 when the technique of Patent Document 3 is applied to a scroll compressor that employs a differential pressure oil supply method as in Patent Document 1 and Patent Document 2, it flows out from the upper end opening of the oil supply path of the main shaft toward the internal space of the boss part.
  • the refrigerating machine oil directly flows into the innermost chamber together with the refrigerant without lubricating the rocking bearing provided in the internal space of the boss portion. For this reason, there is a problem that the oil cannot be supplied to the rocking bearing shaft provided in the internal space of the boss portion, and the rocking shaft portion of the main shaft is seized, resulting in a decrease in reliability.
  • the present invention has been made to solve the above problems, and in a scroll compressor provided with a discharge valve mechanism, it is possible to avoid the vacuum state of the innermost chamber during the reverse rotation operation of the electric motor and to reverse the electric motor.
  • An object of the present invention is to provide a scroll compressor capable of supplying oil to a bearing during operation.
  • a scroll compressor according to the present invention is provided with a sealed container, a fixed scroll and a swing provided in the sealed container, in which plate-like spiral teeth provided on each base plate portion are combined with each other to form a plurality of compression chambers.
  • a compression mechanism portion having a moving scroll, an electric motor for driving the compression mechanism portion, and a boss portion provided on a surface opposite to the plate-like spiral teeth on the base plate portion of the swing scroll, can be freely rotated via a swing bearing.
  • the base plate portion of the orbiting scroll is provided with a path that connects the outer space of the boss portion and the innermost chamber, so that the pressure in the outer space of the boss portion is drawn into the innermost chamber during the reverse rotation operation of the motor.
  • the vacuum state of the innermost chamber can be avoided.
  • the pressure in the external space of the boss part is lowered by the flow of the refrigerant from the external space of the boss part to the innermost chamber, and the pressure in the external space of the boss part is made lower than the pressure in the sealed container, so that the differential pressure required for refueling Therefore, it is possible to obtain a highly reliable scroll compressor that can supply oil to each part of the compressor during the reverse rotation operation.
  • FIG. 1 It is a schematic sectional drawing which shows the structure of the scroll compressor which concerns on Embodiment 1 of this invention. It is a schematic sectional drawing of the compression mechanism part of FIG. 1, and its periphery. It is the schematic which showed the flow of the refrigerating machine oil at the time of differential pressure oil supply in the scroll compressor which concerns on Embodiment 1 of this invention, and the flow of the pressure of the boss
  • Graph A showing a change in pressure adjustment capability of the external space of the boss according to the diameter of the pressure path during the reverse rotation operation of the scroll compressor according to Embodiment 1 of the present invention, and during the forward rotation operation of the scroll compressor
  • FIG. 3 is a graph B showing a change in compressor efficiency according to the diameter of a pressure path. It is a schematic sectional drawing which shows the principal part of the scroll compressor which concerns on Embodiment 2 of this invention.
  • FIG. 1 is a schematic cross-sectional view showing the structure of a scroll compressor according to Embodiment 1 of the present invention.
  • the same reference numerals denote the same or equivalent parts, which are common throughout the entire specification.
  • the forms of the constituent elements appearing in the entire specification are merely examples and are not limited to these descriptions.
  • the level of temperature, pressure, etc. is not particularly determined in relation to absolute values, but is relatively determined in terms of the state, operation, etc. of the system, apparatus, etc.
  • the scroll compressor 100 has at least a compression mechanism unit 10 and an electric motor 20 in a sealed container 100a.
  • the compression mechanism unit 10 and the electric motor 20 are connected by a main shaft 6 that transmits the rotational force generated by the electric motor 20 to the compression mechanism unit 10.
  • the sealed container 100a is provided with a suction pipe 12 for sucking gas and a discharge pipe 13 for discharging compressed gas.
  • the lower part of the sealed container 100a is an oil reservoir for storing the refrigerating machine oil 5.
  • the refrigerating machine oil 5 accumulated in the oil sump is formed by penetrating in the axial direction of the main shaft 6 by a differential pressure described later. It is sucked up from the lower end opening of the path 6d, passes through the oil supply path 6d, and is supplied to the sliding parts of the rocking bearing 2e, the main bearing 3c, the auxiliary main bearing 3d, and the compression mechanism section 10.
  • the compression mechanism unit 10 includes a fixed scroll 1 and a swing scroll 2.
  • the fixed scroll 1 includes a base plate portion 1a and plate-like spiral teeth 1b that are spiral projections provided upright on one surface of the base plate portion 1a, and a bolt (not shown) is attached to the sealed container 100a. It is fixed by etc.
  • the orbiting scroll 2 includes a base plate portion 2a and plate-like spiral teeth 2b that are spiral projections provided upright on one surface of the base plate portion 2a. 6a is swingably supported.
  • the plate-like spiral teeth 1b of the fixed scroll 1 and the plate-like spiral teeth 2b of the swing scroll 2 are combined so as to mesh with each other, and are separated from each other by the combined plate-like spiral teeth 1b and plate-like spiral teeth 2b.
  • the plurality of spaces serve as a plurality of compression chambers 14 for compressing the refrigerant gas.
  • the plurality of compression chambers 14 are located on the outer periphery of the plurality of compression chambers 14 and communicate with the suction pipe 12 from the compression chamber suction space 14a to the outermost chamber 14b located on the outermost side among the plurality of compression chambers 14. And the pressure of the refrigerant gas is increased as the main shaft 6 moves to the center as the main shaft 6 rotates.
  • a discharge port 1d that discharges the compressed refrigerant to a high pressure is formed.
  • the discharge port 1d covers the discharge port 1d, and the refrigerant gas flows from the innermost chamber 14c located on the radially innermost side among the plurality of compression chambers 14 toward the inner space of the sealed container 100a through the discharge port 1d.
  • a discharge valve mechanism 9 that prevents the flow in the opposite direction is disposed.
  • the discharge valve mechanism 9 has a discharge valve 9a made of a leaf spring. When the refrigerant is compressed to a predetermined pressure in the compression chamber 14, the discharge valve 9a is pushed open against its elastic force and discharged from the discharge port. 1d is opened. Then, the compressed refrigerant is discharged from the opened discharge port 1 d to the sealed container internal space 100 b and discharged to the outside of the scroll compressor 100 through the discharge pipe 13. Therefore, the sealed container internal space 100b is a high-pressure space.
  • a hollow cylindrical boss 2d is formed at the center of the surface (the lower surface in FIG. 1) opposite to the surface on which the plate-like spiral teeth 2b are formed in the base plate 2a of the orbiting scroll 2.
  • a rocking bearing 2e is disposed on the inner surface of the boss 2d.
  • a thrust surface 2f that is slidable against the thrust bearing 3a of the movable frame 3 is formed on the outer peripheral portion of the surface (the lower surface in FIG. 1) on the same side as the boss portion 2d in the base plate portion 2a. .
  • an Oldham mechanism 8 is arranged between the fixed scroll 1 and the swing scroll 2 to prevent the swing scroll 2 from rotating and to regulate the posture.
  • two pairs of Oldham guide grooves 1c are formed in a substantially straight line on the outer peripheral portion of one surface (the lower surface in FIG. 1) of the base plate portion 1a of the fixed scroll 1.
  • a pair of two fixed-side keys 8 a of the Oldham mechanism 8 is engaged with the Oldham guide groove 1 c so as to be slidable in the circumferential direction of the main shaft 6.
  • a pair of Oldham guide grooves 2c having a phase difference of about 90 degrees with the Oldham guide groove 1c of the fixed scroll 1 are formed on the outer peripheral portion of the base plate portion 2a of the orbiting scroll 2 in a substantially straight line. ing.
  • a pair of swing-side keys 8b of the Oldham mechanism 8 is engaged with the Oldham guide groove 2c so as to be slidable in the circumferential direction of the main shaft 6.
  • a surface 3b on which the Oldham mechanism annular portion 8c reciprocates is formed outside the thrust bearing 3a of the movable frame 3.
  • the fixed-side key 8a and the swing-side key 8b of the Oldham mechanism 8 are engaged with the Oldham guide groove 1c of the fixed scroll 1 and the Oldham guide groove 2c of the swing scroll 2 so as to be reciprocally slidable.
  • the rotation of the dynamic scroll 2 is prevented.
  • the electric motor 20 includes an electric motor stator 21 formed in a ring shape, and an electric motor rotor 22 supported so as to be able to rotate inside the electric motor stator 21.
  • the electric motor rotor 22 is shrink-fitted between a later-described auxiliary shaft portion 6c of the main shaft 6 and the main shaft portion 6b.
  • the fixed frame 4 and the subframe 7 are fixed to the sealed container 100a so as to face each other with the electric motor 20 interposed therebetween.
  • a movable frame 3 is disposed inside the fixed frame 4, and a main bearing 3 c and an auxiliary main bearing 3 d are disposed in the center of the movable frame 3 and the subframe 7.
  • the main shaft 6 is rotatably supported by a main bearing 3c, an auxiliary main bearing 3d, and a sub bearing 7a provided at the center of the movable frame 3 and the sub frame 7.
  • the main shaft 6 is composed of a swinging shaft portion 6 a above the main shaft 6, a main shaft portion 6 b, and a sub shaft portion 6 c below the main shaft 6.
  • the oscillating scroll 2 is fitted to the oscillating shaft portion 6a via the oscillating bearing 2e, and the oscillating scroll 2 is oscillated by the rotation of the main shaft 6.
  • the main shaft portion 6 b is fitted to the main bearing 3 c and slides with the main bearing 3 c through an oil film formed by the refrigerator oil 5.
  • the fixed frame 4 has a shape in which a plurality of cylindrical portions having different diameters are connected in the axial direction, and is configured such that the diameter becomes smaller toward the electric motor 20 side (lower side in FIG. 1).
  • the upper fitting cylindrical portion 4 a on the fixed scroll 4 side (the upper side in FIG. 1) is engaged with the upper fitting cylindrical portion 3 e of the movable frame 3.
  • the lower fitting cylindrical portion 4 b of the fixed frame 4 on the electric motor 20 side (lower side in FIG. 1) is engaged with the lower fitting cylindrical portion 3 f of the movable frame 3.
  • FIG. 2 is a schematic cross-sectional view of the compression mechanism portion of FIG. 1 and its surroundings.
  • the compressor suction space 12a has a gas atmosphere (suction pressure).
  • a space surrounded by the base plate portion 2a and the movable frame 3 of the orbiting scroll 2 and on the inner peripheral side of the thrust bearing 3a is a low pressure space 2g for realizing differential pressure oil supply. It has become. Since the boss portion 2d of the orbiting scroll 2 is located in the low pressure space 2g and the low pressure space 2g is located outside the boss portion 2d, the low pressure space 2g is hereinafter referred to as a boss portion external space 2g.
  • the movable frame 3 is formed with a communication passage 3h penetrating in the axial direction.
  • the upper end of the communication passage 3 h communicates with the extraction hole 2 j of the base plate portion 2 a of the orbiting scroll 2, and the lower end communicates with the space between the movable frame 3 and the fixed frame 4.
  • the movable frame 3 is lifted by the intermediate pressure in the compression chamber 14 acting as the back pressure of the movable frame 3 through the extraction hole 2j and the communication passage 3h, and the swinging scroll 2 is pressed against the fixed scroll 1. I do.
  • the movable frame 3 is provided with a movable frame check valve mechanism 3g that allows a one-way flow from the boss portion outer space 2g to the compressor suction space 12a.
  • the base plate portion 2a of the orbiting scroll 2 is provided with a pressure path 2h, which is a characteristic portion of the present invention, that communicates the innermost chamber 14c and the boss portion outer space 2g.
  • a pressure path 2h is provided to prevent a pressure drop in the compression chamber 14 when the compression chamber 14 is in a vacuum state during the reverse rotation operation of the scroll compressor 100. Is. Note that the processing hole in the pressure path 2h is closed by the plug 2i.
  • FIG. 3 is a schematic diagram showing the flow of refrigeration oil during differential pressure oil supply in the scroll compressor according to Embodiment 1 of the present invention, and the flow of pressure in the external space of the boss portion during differential pressure oil supply.
  • the white arrow 11 a indicates the flow of the refrigerating machine oil 5 to each part of the compressor.
  • the flow of the refrigerating machine oil 5 is the same regardless of whether the scroll compressor 100 is operated forward or reverse.
  • the dotted line arrows indicate the refrigerant flow during the forward rotation operation
  • the solid line arrows indicate the refrigerant flow during the reverse rotation operation.
  • the outermost chamber 14b decreases in volume while moving from the outer peripheral portion toward the center in accordance with the swing motion of the swing scroll 2. For this reason, the refrigerant gas taken into the outermost chamber 14 b is compressed as the volume of the compression chamber 14 decreases.
  • the compressed refrigerant gas is discharged from the discharge port 1d provided in the fixed scroll 1 into the sealed container 100a through the discharge valve mechanism 9. Then, the refrigerant gas discharged into the sealed container 100a is discharged from the discharge pipe 13 to the refrigerant circuit outside the sealed container 100a.
  • the external space 2g of the boss part is affected by the discharge pressure in the sealed container 100a, and the refrigerant flow (from the external space 2g of the boss part 2g to the compressor suction space 12a by the movable frame check valve mechanism 3g ( The dotted arrows in FIG. 3 are allowed.
  • the boss portion outer space 2g is controlled to an intermediate pressure between the suction pressure and the discharge pressure.
  • the refrigerating machine oil 5 stored in the lower portion of the sealed container 100a which is a high-pressure space, is supplied with a differential pressure (the high pressure in the sealed container 100a and the intermediate pressure of the boss portion outer space 2g). Ascend 6d.
  • a plurality of oil supply passages are formed in the main shaft 6 so as to communicate with the oil supply passage 6d in the radial direction, and the refrigerating machine oil 5 rising up the oil supply passage 6d is supplied to each of the oil supply passages (not shown).
  • the oil is supplied to each of the auxiliary bearing 7a, the main bearing 3c and the auxiliary main bearing 3d.
  • the refrigerating machine oil 5 flowing out from the upper end opening of the oil supply path 6d is supplied to the rocking bearing 2e and then flows to the boss portion external space 2g.
  • the pressure in the outermost chamber 14b and the compression chamber suction space 14a is higher than the pressure in the outermost chamber 14b and the compression chamber suction space 14a during the forward rotation operation. Further, since the refrigerant gas in the innermost chamber 14c does not become the discharge pressure during the reverse rotation operation, the refrigerant gas is not discharged into the sealed container 100a through the discharge port 1d. Therefore, the pressure in the sealed container 100a does not increase.
  • the pressure of the boss part external space 2g affected by the pressure in the sealed container 100a is lower than the pressure of the outermost chamber 14b and the compression chamber suction space 14a, and the reverse of the movable frame provided in the movable frame 3
  • the stop valve mechanism 3g does not operate. That is, there is no refrigerant flow from the boss portion external space 2g to the compression chamber suction space 14a.
  • the innermost chamber 14c does not become high pressure as during normal rotation operation, so the discharge valve mechanism 9 remains closed. Therefore, during the reverse rotation operation of the electric motor 20, the innermost chamber 14c and the boss portion outer space 2g communicating with the innermost chamber 14c are closed spaces. Then, as described above, the refrigerant in the innermost chamber 14c is carried in a direction opposite to that during the forward rotation operation, so that the innermost chamber 14c is in a vacuum state or a vacuum state.
  • the refrigerant gas and / or the refrigeration oil 5 in the outer space 2g of the boss part, or both, as indicated by solid arrows in FIG. It flows into the innermost chamber 14c from the boss portion outer space 2g through the pressure path 2h. Thereby, the pressure drop of the innermost chamber 14c can be prevented and a vacuum state can be avoided.
  • the pressure in the boss portion outer space 2g is lower than the pressure in the sealed container 100a. For this reason, the same differential pressure refueling as that during the forward rotation operation of the compressor is executed.
  • the pressure path 2h is desirably 2 mm or less and more than 0 mm.
  • FIG. 4 is a graph A showing a change in pressure adjustment capability of the external space of the boss portion according to the diameter of the pressure path during the reverse rotation operation of the scroll compressor according to the first embodiment of the present invention. It is the figure which showed the graph B which shows the change of the compressor efficiency according to the diameter of the pressure path
  • the horizontal axis represents the pressure path diameter ⁇ [mm]
  • the right vertical axis represents the pressure adjustment capability [%] during the reverse rotation operation
  • the left vertical axis represents the compressor efficiency [%].
  • the compressor efficiency during the forward rotation operation of the scroll compressor 100 decreases as the diameter of the pressure path 2h increases.
  • the pressure adjustment capability of the boss portion external space 2g during the reverse rotation operation of the scroll compressor 100 increases as the diameter of the pressure path 2h increases.
  • pressure adjustment capacity 100% a state in which a necessary amount of refrigerant can be supplied to the innermost chamber 14c in order to prevent the inside of the compression chamber 14 from being evacuated even during reverse rotation operation.
  • the compressor adjustment capacity is 90% or more, the refrigerant can be supplied to the innermost chamber 14c even in the case of reverse operation, and the compressor can be stopped without damaging the scroll compressor 100 by the vacuum operation. Sufficient time can be secured.
  • the reduction of the compressor efficiency is less than 1%, it is at a level where there is no problem in actual operation.
  • the pressure path 2h is desirably ⁇ 2 mm or less.
  • the boss portion outer space 2g and the innermost chamber 14c are configured to communicate with each other through the pressure path 2h, so that oil is supplied to each portion of the compressor even during reverse rotation operation. Abnormal wear of the shaft and the bearing can be prevented. Moreover, the highly reliable scroll compressor 100 which can avoid the vacuum state of the compression chamber 14 and can prevent abnormal wear of the spiral teeth of the fixed scroll 1 and the swing scroll 2 can be obtained.
  • Embodiment 2 FIG. In the second embodiment, the flow of the refrigerant from the innermost chamber 14c to the boss portion outer space 2g is blocked in the pressure path 2h in the first embodiment.
  • FIG. 5 is a schematic cross-sectional view showing the main part of the scroll compressor according to Embodiment 2 of the present invention.
  • the scroll compressor 100 according to the second embodiment further includes a pressure path check valve mechanism 2k in the pressure path 2h in addition to the scroll compressor 100 according to the first embodiment.
  • the pressure path check valve mechanism 2k allows the refrigerant gas to flow from the boss portion outer space 2g toward the innermost chamber 14c, and prevents the refrigerant gas from flowing in the opposite direction.
  • positioning the pressure path check valve mechanism 2k is obstruct
  • the scroll compressor 100 according to the second embodiment configured as described above has the same effect as that of the first embodiment, and further includes the pressure path check valve mechanism 2k in the pressure path 2h.
  • the effect is obtained. That is, it is possible to prevent the refrigerant gas from leaking from the innermost chamber 14c to the boss portion external space 2g during the forward rotation operation, and it is possible to prevent a decrease in compressor efficiency.
  • the pressure path check valve mechanism 2k when the pressure path check valve mechanism 2k is installed in a location close to the innermost chamber 14c in the pressure path 2h, it is possible to reduce the dead volume of the compression chamber 14 and further prevent a decrease in compressor efficiency. it can. Therefore, it is desirable that the pressure path check valve mechanism 2k be installed at a location as close to the innermost chamber 14c as structurally and material strength allows.
  • the scroll compressor 100 of the second embodiment has a reliability equivalent to that of the scroll compressor 100 shown in the first embodiment, and a more efficient compressor can be obtained.

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

Abstract

La présente invention comprend : un récipient étanche vis-à-vis de l'air (100a) ; une section de mécanisme de compression (10) qui est disposée à l'intérieur du récipient étanche vis-à-vis de l'air (100a) et qui a une volute fixe (1) et une volute oscillante (2) dans lesquelles des dents en spirale en forme de plaque (1b, 2b) disposées sur des parties de plaque de base individuelles (1a, 2a) sont amenées les unes contre les autres et une pluralité de chambres de compression (14) sont formées ; une partie de protubérance (2d) qui est disposée sur la surface du côté opposé aux dents en spirale en forme de plaque (2b) dans la partie de plaque de base (2a) de la volute oscillante (2) ; et un mécanisme de soupape de décharge (9) pour recouvrir un orifice d'évacuation (1d) de la volute fixe (1), permettant l'écoulement de gaz réfrigérant à partir des chambres de compression (14) à travers l'orifice de décharge (1d) jusqu'à l'espace interne du récipient étanche vis-à-vis de l'air (100a), et empêchant un écoulement dans la direction inverse. La partie de plaque de base (2a) de la volute oscillante (2) a un canal de pression (2h) par l'intermédiaire duquel une chambre située le plus à l'intérieur (14c) positionnée le plus loin radialement vers l'intérieur parmi la pluralité de chambres de compression (14) et un espace externe (2g) de la partie de protubérance (2d) de la volute oscillante (2) communiquent.
PCT/JP2015/064803 2015-05-22 2015-05-22 Compresseur à volutes WO2016189598A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
PCT/JP2015/064803 WO2016189598A1 (fr) 2015-05-22 2015-05-22 Compresseur à volutes
JP2017520076A JP6395929B2 (ja) 2015-05-22 2015-05-22 スクロール圧縮機
CN201610258465.6A CN106168212B (zh) 2015-05-22 2016-04-22 涡旋式压缩机
CN201620350387.8U CN205638916U (zh) 2015-05-22 2016-04-22 涡旋式压缩机

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2015/064803 WO2016189598A1 (fr) 2015-05-22 2015-05-22 Compresseur à volutes

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021204592A1 (fr) * 2020-04-09 2021-10-14 OET GmbH Machine à déplacement positif, procédé, système de climatisation de véhicule, et véhicule associé
EP4269799A1 (fr) * 2022-04-29 2023-11-01 Robert Bosch GmbH Plaque à spirales orbitale et compresseur à spirales

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JP6395929B2 (ja) * 2015-05-22 2018-09-26 三菱電機株式会社 スクロール圧縮機
US11933306B2 (en) * 2019-06-28 2024-03-19 Mitsubishi Electric Corporation Scroll compressor and refrigeration cycle apparatus

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JPH0246089U (fr) * 1988-09-21 1990-03-29
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JP2004239070A (ja) * 2003-02-03 2004-08-26 Daikin Ind Ltd スクロール型圧縮機
JP2011052603A (ja) * 2009-09-02 2011-03-17 Daikin Industries Ltd スクロール圧縮機
US20130121865A1 (en) * 2011-11-09 2013-05-16 Kitae Jang Scroll compressor
JP2014088852A (ja) * 2012-10-31 2014-05-15 Mitsubishi Heavy Ind Ltd スクロール型圧縮機

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JP4156494B2 (ja) * 2003-11-06 2008-09-24 株式会社デンソー スクロール型圧縮機
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Publication number Priority date Publication date Assignee Title
JPS59115488A (ja) * 1982-12-22 1984-07-03 Hitachi Ltd 密閉形スクロ−ル圧縮機の軸受装置
JPS59123686U (ja) * 1983-02-07 1984-08-20 シャープ株式会社 スクロ−ル圧縮機
JPS6385277A (ja) * 1986-09-29 1988-04-15 Toshiba Corp スクロ−ル容積形機械
JPH0246089U (fr) * 1988-09-21 1990-03-29
JPH0491291U (fr) * 1990-12-20 1992-08-10
JP2004239070A (ja) * 2003-02-03 2004-08-26 Daikin Ind Ltd スクロール型圧縮機
JP2011052603A (ja) * 2009-09-02 2011-03-17 Daikin Industries Ltd スクロール圧縮機
US20130121865A1 (en) * 2011-11-09 2013-05-16 Kitae Jang Scroll compressor
JP2014088852A (ja) * 2012-10-31 2014-05-15 Mitsubishi Heavy Ind Ltd スクロール型圧縮機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021204592A1 (fr) * 2020-04-09 2021-10-14 OET GmbH Machine à déplacement positif, procédé, système de climatisation de véhicule, et véhicule associé
EP4269799A1 (fr) * 2022-04-29 2023-11-01 Robert Bosch GmbH Plaque à spirales orbitale et compresseur à spirales

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JP6395929B2 (ja) 2018-09-26
JPWO2016189598A1 (ja) 2018-01-18
CN205638916U (zh) 2016-10-12
CN106168212A (zh) 2016-11-30
CN106168212B (zh) 2021-01-01

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