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WO2015059833A1 - Machine à fluide à volutes - Google Patents

Machine à fluide à volutes Download PDF

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Publication number
WO2015059833A1
WO2015059833A1 PCT/JP2013/079033 JP2013079033W WO2015059833A1 WO 2015059833 A1 WO2015059833 A1 WO 2015059833A1 JP 2013079033 W JP2013079033 W JP 2013079033W WO 2015059833 A1 WO2015059833 A1 WO 2015059833A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
frame
scroll
valve
hole
Prior art date
Application number
PCT/JP2013/079033
Other languages
English (en)
Japanese (ja)
Inventor
祐司 ▲高▼村
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 JP2015543680A priority Critical patent/JP6120982B2/ja
Priority to PCT/JP2013/079033 priority patent/WO2015059833A1/fr
Publication of WO2015059833A1 publication Critical patent/WO2015059833A1/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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • 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
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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

Definitions

  • the present invention relates to a scroll fluid machine such as a scroll compressor and a scroll pump.
  • the scroll compressor is provided with an oil pump that is operated by the rotation of the main shaft and pumps up the oil stored in the oil sump at the bottom of the shell.
  • the oil pumped up by the oil pump is supplied to sliding parts such as a rocking bearing, a main bearing, and a sub-bearing through an oil supply vertical hole penetrating the main shaft in the longitudinal direction.
  • the oil that has finished lubricating the rocking bearing is stored inside the frame and used for lubrication of the Oldham coupling and the thrust surface of the rocking scroll, cooling the rocking bearing, and the main bearing.
  • Patent Document 1 discloses a scroll compressor provided with a bypass hole that branches from an oil supply hole of a main shaft and opens to the outside of the main shaft, and a valve that opens and closes the bypass hole with a predetermined hydraulic pressure.
  • the valve is opened with a hydraulic pressure exceeding a predetermined pressure, and excess oil is discharged from the bypass hole and returned to the oil sump.
  • the fluid taken into the shell from the suction pipe is taken into the frame through the suction port.
  • the space in the frame is provided with fixed vortex and oscillating vortex that are alternately combined, and the oscillating vortex oscillates with respect to the fixed vortex.
  • the fluid taken into the frame is compressed in a compression chamber formed by a fixed vortex and an oscillating vortex, and is discharged to the outside of the scroll compressor through a discharge chamber, a muffler, and a discharge pipe.
  • the driving force for compressing the fluid is applied to the oscillating spiral by the rotation of the main shaft integrated with the rotor of the electric motor.
  • the main shaft and the oscillating vortex are connected via an oscillating bearing, and the rotation of the oscillating vortex is regulated by an Oldham coupling.
  • the main shaft is supported by a main bearing and a sub bearing.
  • the frame is a housing for storing a fixed spiral and a swing spiral, and has a thrust bearing and a main bearing that support an axial load acting on the swing spiral.
  • the main bearing, the rocking bearing, the auxiliary bearing, the thrust bearing, and the Oldham coupling are lubricated with oil.
  • the oil is pumped from the bottom of the shell by an oil pump that uses the rotation of the main shaft as a driving force.
  • the oil pump is connected to the lower end of the main shaft, and supplies the oil pumped up from the bottom of the shell to each sliding portion through an oil supply vertical hole formed in the main shaft.
  • the amount of oil pumped up by the oil pump increases as the rotational speed of the compressor increases.
  • Oil supply to the rocking bearing is performed by an oil supply vertical hole in the main shaft.
  • Oil supply to the main bearing and the sub-bearing is performed by an oil supply vertical hole and an oil supply horizontal hole branched in an orthogonal direction from the oil supply vertical hole in the main shaft.
  • the oil that has lubricated the main and sub bearings drips down and returns to the sump at the bottom of the shell.
  • the oil that has lubricated the rocking bearing is stored in the space in the frame.
  • the oil accumulated in the space in the frame is lubricated to the thrust bearing, lubricated to the Oldham coupling, lubricated to the spiral sliding part (sliding part of the fixed spiral and swinging spiral), lubricated to the main bearing, It plays a role of cooling the dynamic bearing and the main bearing.
  • An oil drain pipe is connected to the space in the frame. Excess oil in the space in the frame is returned from the space in the frame to the oil sump at the bottom of the shell through the oil drain pipe.
  • the present invention has been made to solve the above-described problems, and provides a scroll fluid machine capable of appropriately discharging excess oil in a frame and suppressing an increase in oil rising. With the goal.
  • a scroll fluid machine is formed between a fixed scroll and a swing scroll provided in a container, a frame that supports the swing scroll in a swingable manner, and the frame and the swing scroll.
  • the oil drain valve opens when the hydraulic pressure in the space in the frame rises, excess oil in the frame can be discharged out of the frame from the oil drain hole. Therefore, even if the rotation speed of the main shaft increases and the amount of oil pumped up increases, it is possible to prevent an excessive increase in the hydraulic pressure in the space in the frame.
  • the centrifugal force does not act on the oil drain valve unlike the configuration in which the oil drain valve is provided on the rotating parts such as the main shaft. Therefore, since it is not necessary to consider a centrifugal force as a load which acts on a drain valve, the opening degree characteristic of a drain valve can be adjusted easily. Further, since centrifugal force does not act on the oil discharge valve, the strength and reliability of the oil discharge valve can be ensured. Therefore, according to the present invention, surplus oil in the frame can be appropriately discharged out of the frame.
  • the oil drain hole is fixed to the container, it is possible to prevent the oil from being scattered as compared with a configuration in which oil is discharged from the outer peripheral surface of the rotating main shaft. Therefore, it is possible to suppress the oil from being wound up by the refrigerant, and it is possible to suppress an increase in the oil.
  • FIG. 1 is a schematic cross-sectional view showing an overall configuration of a scroll compressor according to Embodiment 1 of the present invention. It is sectional drawing which expands and shows a part of scroll compressor which concerns on Embodiment 1 of this invention. It is a figure which shows the flow of the oil in the scroll compressor which concerns on Embodiment 1 of this invention. It is a figure which shows the flow of the oil in space 6c vicinity in the frame in the scroll compressor which concerns on Embodiment 1 of this invention. It is sectional drawing which expands and shows a part of scroll compressor which concerns on Embodiment 2 of this invention. It is sectional drawing which expands and shows a part of scroll compressor which concerns on the modification of Embodiment 2 of this invention.
  • FIG. 1 is a schematic cross-sectional view showing the overall configuration of the scroll compressor according to the present embodiment.
  • FIG. 2 is an enlarged cross-sectional view of a part of the scroll compressor according to the present embodiment.
  • the scroll compressor sucks a fluid (for example, a refrigerant), compresses the fluid, and discharges it as a high-temperature and high-pressure state.
  • a scroll compressor becomes one of the components of the refrigerating cycle apparatus used for various industrial machines, such as a refrigerator, a freezer, a vending machine, an air conditioning apparatus, a freezing apparatus, or a water heater.
  • the dimensional relationship and shape of each component may differ from the actual ones.
  • the scroll compressor has a configuration in which a compression mechanism portion 40 that compresses a fluid and an electric motor portion 50 that drives the compression mechanism portion 40 are accommodated in an airtight container 60 (shell).
  • the sealed container 60 has a configuration in which the upper shell 24, the middle shell 25, and the lower shell 26 are airtightly joined by welding or the like.
  • An oil sump 18 is formed at the bottom of the lower shell 26.
  • the oil sump 18 stores oil (refrigeration machine oil) that lubricates each sliding part in the scroll compressor.
  • a suction pipe 7 is connected to the middle shell 25 as a suction port for sucking low-pressure refrigerant into the sealed container 60.
  • a discharge pipe 1 is connected to the upper shell 24 as a discharge port for discharging the compressed refrigerant to the outside of the sealed container 60.
  • the electric motor unit 50 drives the rocking scroll 5 of the compression mechanism unit 40 via the main shaft 14 in order to compress the refrigerant gas by the compression mechanism unit 40.
  • the electric motor unit 50 includes a stator 11 fixed to the inner peripheral surface of the sealed container 60 and a rotor 12 fixed to the main shaft 14.
  • the rotor 12 is rotationally driven by energizing the stator 11 and rotates the main shaft 14 that transmits the driving force to the orbiting scroll 5.
  • a power source for supplying power to the stator 11 for example, an inverter power source is used that can change the driving rotational speed within a predetermined range in order to make the refrigerant circulation amount variable.
  • an eccentric shaft portion 29 that is rotatably fitted to the rocking bearing 21 of the rocking scroll 5 is formed.
  • an oil supply vertical hole 14 a serving as a supply channel for oil stored in the oil sump 18 is provided so as to penetrate from the lower end to the upper end along the longitudinal direction (axial direction) of the main shaft 14. Yes.
  • oil supply lateral holes 14 b and 14 c that branch in an orthogonal direction from the oil supply vertical hole 14 a and extend to the outer peripheral surface of the main shaft 14 along the radial direction of the main shaft 14 are provided in the main shaft 14.
  • the oil supply lateral hole 14b is provided near or above a main bearing 19 described later
  • the oil supply horizontal hole 14c is provided near or above a ball bearing 16 (sub bearing) described later.
  • An oil pump 17 is provided at the lower end of the main shaft 14.
  • the oil pump 17 pumps up the oil in the oil sump 18 using the rotation of the main shaft 14 as a driving force.
  • the amount of oil pumped up by the oil pump 17 increases as the rotational speed of the main shaft 14 increases.
  • the pumped-up oil is supplied to each sliding portion in the scroll compressor and a frame inner space 6c described later through the oil supply vertical holes 14a and the oil supply horizontal holes 14b and 14c.
  • a first balancer 10 is provided above the main shaft 14.
  • a second balancer 13 is provided below the rotor 12.
  • the first balancer 10 and the second balancer 13 rotate together with the main shaft 14 and the rotor 12, and have a function of balancing the rocking scroll 5 with respect to the rotation center of the main shaft 14.
  • the first balancer 10 is covered with a balancer cover 9 attached to the lower part of the frame 6.
  • the compression mechanism unit 40 has a fixed scroll 4 and a swing scroll 5.
  • the fixed scroll 4 is fixed to the frame 6 fixedly supported by the middle shell 25.
  • the fixed scroll 4 includes an end plate 4a and a spiral portion 4b that is an involute curved projection provided on the lower surface of the end plate 4a.
  • a discharge port 30 is formed at the center of the fixed scroll 4 to discharge the refrigerant gas that has been compressed to a high pressure.
  • a discharge chamber 3 and a muffler 2 are provided on the outlet side of the discharge port 30.
  • the oscillating scroll 5 performs an oscillating motion (revolving orbiting motion) without rotating with respect to the fixed scroll 4.
  • the orbiting scroll 5 includes an end plate 5a and a spiral portion 5b that is an involute curved projection provided on the upper surface of the end plate 5a.
  • a thrust bearing 31 is provided on the surface of the orbiting scroll 5 opposite to the surface where the spiral portion 5b is formed (on the side opposite to the compression chamber).
  • the orbiting scroll 5 is supported in the axial direction by the thrust surface of the frame 6 via the thrust bearing 31.
  • a bottomed cylindrical rocking bearing 21 is formed at a substantially central portion of the surface of the rocking scroll 5 on the side opposite to the compression chamber.
  • the rocking bearing 21 accommodates a slider 22 that supports the rocking scroll 5 so that the rocking scroll 5 can revolve.
  • An eccentric shaft portion 29 provided at the upper end of the main shaft 14 is inserted into the slider 22.
  • the fixed scroll 4 and the orbiting scroll 5 are mounted in the sealed container 60 in a state in which the spiral part 4b and the spiral part 5b whose winding directions are opposite to each other are meshed with each other.
  • the volume changes between the spiral portion 4b and the spiral portion 5b as the swing scroll 5 swings.
  • a compression chamber is formed.
  • An Oldham joint 23 is disposed between the orbiting scroll 5 and the frame 6 for preventing the rotation of the orbiting scroll 5 during the orbiting movement.
  • the key portion formed on the upper surface of the Oldham joint 23 is slidably received in the Oldham groove provided in the swing scroll 5, and the key portion formed on the lower surface is provided by the Oldham provided in the frame 6. It is slidably received in the groove.
  • the frame 6 is fixed to the inner peripheral surface of the sealed container 60.
  • the frame 6 fixedly supports the fixed scroll 4 and supports the swing scroll 5 through a thrust bearing 31 so as to be swingable. Between the frame 6 and the orbiting scroll 5, an in-frame space 6c is formed. A predetermined amount of the oil supplied through the oil supply vertical hole 14a can be stored in the frame internal space 6c.
  • an oil drain hole 6a for discharging excess oil in the frame internal space 6c is formed.
  • One end of an oil drain pipe 8a for returning the oil to the oil sump 18 is connected to the oil drain hole 6a.
  • the other end of the oil drain pipe 8 a extends through the stator 11 and above the oil sump 18.
  • the oil discharge hole 6a and the oil discharge pipe 8a are not provided with an oil discharge valve. That is, the oil drain hole 6a and the oil drain pipe 8a constitute an oil drain passage that is always open.
  • the oil receiver 27 is attached to the outside of the frame 6.
  • the space 6c in the frame and the space in the oil receiver 27 communicate with each other via an oil drain hole 6b formed through the frame 6 at a different location from the oil drain hole 6a.
  • the oil drain hole 6 b is configured to discharge excess oil in the frame inner space 6 c to the oil receiver 27 outside the frame 6.
  • the oil receiver 27 is configured to temporarily receive the oil discharged from the oil discharge hole 6 b without being exposed to the flow of the fluid (refrigerant) in the sealed container 60.
  • An outlet on the oil receiver 27 side of the oil drain hole 6 b is formed on a vertical surface outside the frame 6.
  • An oil discharge valve 28 having a reed valve structure in which one end of a rigid leaf spring portion is fixed is provided at the oil receiver 27 side outlet of the oil discharge hole 6b.
  • the oil drain hole 6b is closed from the oil receiver 27 side by a drain valve 28 having a reed valve structure.
  • the oil discharge valve 28 is adjusted so as to start to open when the hydraulic pressure P in the frame internal space 6c increases to reach a predetermined pressure P ′ by deforming the leaf spring portion with a predetermined deformation amount, for example. ing.
  • One end of an oil drain pipe 8 b for returning oil to the oil sump 18 is connected to the bottom of the oil receiver 27.
  • the oil drain pipe 8 b is provided between the oil receiver 27 and the oil reservoir 18, and the other end of the oil drain pipe 8 b extends through the stator 11 and above the oil reservoir 18.
  • the oil drain hole 6b and the oil drain pipe 8b constitute an oil drain passage that is opened only when the hydraulic pressure P in the frame inner space 6c rises above the pressure P '.
  • the frame 6 rotatably supports an upper portion of the main shaft 14 in the vicinity of the eccentric shaft portion 29 via a main bearing 19 provided in a through hole in the center portion.
  • a sleeve 20 for smoothly rotating the main shaft 14 penetrating the main bearing 19 is rotatably accommodated in the main bearing 19.
  • the subframe 15 is provided below the frame 6 and is fixed to the inner peripheral surface of the sealed container 60.
  • the sub-frame 15 rotatably supports the lower part of the main shaft 14 through a through hole formed in the center.
  • An outer ring of a ball bearing 16 for rotatably supporting the main shaft 14 is press-fitted and fixed in the through hole of the sub frame 15.
  • the low-pressure gas refrigerant in the refrigerant circuit is sucked into the sealed container 60 through the suction pipe 7 and flows into the compression chamber through a suction port (not shown) provided in the frame 6.
  • the refrigerant that has flowed into the compression chamber is compressed along with the swing of the swing scroll 5 to be in a high temperature and high pressure state, flows out of the compression chamber through the discharge port 30, and flows into the discharge chamber 3.
  • the high-pressure gas refrigerant that has flowed into the discharge chamber 3 pushes open a discharge valve provided in the discharge chamber 3 due to a pressure difference, passes through the muffler 2 and the discharge space in the sealed container 60, and passes from the discharge pipe 1 to the sealed container 60. It is discharged outside.
  • the discharged refrigerant circulates in the refrigerant circuit of the refrigeration cycle apparatus and returns to the suction pipe 7 of the scroll compressor as a low-pressure gas refrigerant.
  • FIG. 3 is a diagram illustrating the flow of oil in the scroll compressor.
  • FIG. 4 is a diagram showing the flow of oil in the vicinity of the space 6c in the frame.
  • the arrow in FIG.3 and FIG.4 represents the example of the flow of oil.
  • the oil in the oil sump 18 is pumped up by the oil pump 17 using the rotation of the main shaft 14 as a driving force.
  • the pumped oil flows upward through the oil supply vertical hole 14a.
  • Part of the oil flowing through the oil supply vertical hole 14a lubricates the main bearing 19 through the oil supply lateral hole 14b, and the other part lubricates the ball bearing 16 through the oil supply horizontal hole 14c.
  • the oil after lubricating the main bearing 19 and the ball bearing 16 hangs downward and returns to the oil sump 18.
  • the remaining oil that has not flowed into the oil supply horizontal holes 14b and 14c rises to the upper end in the oil supply vertical hole 14a and lubricates the rocking bearing 21.
  • the ratio between the flow rate of oil flowing into the feed oil horizontal holes 14b and 14c in the middle of the feed oil vertical hole 14a and the flow rate of oil rising to the upper end of the feed oil vertical hole 14a is affected by the pressure state on the downstream side, The flow rate flowing toward the lower pressure side on the downstream side is relatively large.
  • the oil after lubricating the rocking bearing 21 is stored in the space 6c in the frame.
  • the oil stored in the frame inner space 6c plays a role of lubrication of the Oldham joint 23 and the thrust bearing 31, cooling of the rocking bearing 21 and the main bearing 19, and the like.
  • the surplus is discharged to the outside of the frame inner space 6c (outside the frame 6) via the oil discharge hole 6a and the oil discharge pipe 8a that are always open, and the oil reservoir 18 Return to.
  • the amount of oil supplied to the frame inner space 6c through the oil supply vertical hole 14a increases as the rotational speed of the main shaft 14 increases. Further, as the amount of oil supplied increases, the flow rate of the oil discharged through the oil drain hole 6a and the oil drain pipe 8a also increases. When the flow rate of the oil discharged through the oil drain hole 6a and the oil drain pipe 8a increases, the pressure due to the throttle near the inlet of the oil drain hole 6a and the oil drain pipe 8a, the wall friction inside the oil drain pipe 8a, etc. Due to the loss, the hydraulic pressure P in the frame internal space 6c increases. That is, during the high speed operation of the scroll compressor, the rotational speed of the main shaft 14 increases, so that the hydraulic pressure P in the frame inner space 6c increases.
  • the opening characteristic of the oil discharge valve 28 including the pressure P ′ at which the oil discharge valve 28 starts to open and the opening degree change of the oil discharge valve 28 with respect to the increase in the hydraulic pressure in the frame internal space 6c, It can be arbitrarily adjusted depending on the rigidity and the initial deformation amount. At this time, since only the oil pressure P needs to be considered as the load acting on the oil discharge valve 28, the opening degree of the oil discharge valve 28 is compared with a configuration in which the oil discharge valve is attached to the main shaft 14 or the like that is a rotating part. The characteristics can be easily adjusted. The mounting position and mounting direction of the oil drain hole 6a and the oil drain valve 28 can be freely selected.
  • the scroll fluid machine includes the fixed scroll 4 and the swing scroll 5 provided in the hermetic container 60, the frame 6 that supports the swing scroll 5 so as to be swingable, A frame inner space 6c formed between the frame 6 and the orbiting scroll 5, a main shaft 14 for transmitting a driving force to the orbiting scroll 5, and the oil in the oil reservoir 18 by the rotation of the main shaft 14 causes the oil in the oil sump 18 to flow.
  • An oil pump 17 that is pumped up, an oil drain hole 6b that passes through the frame 6 and discharges excess oil in the frame inner space 6c to the outside of the frame 6, and an oil drain hole based on the hydraulic pressure P of the frame inner space 6c.
  • an oil discharge valve 28 that opens and closes 6b.
  • the oil discharge valve 28 opens when the hydraulic pressure P in the frame internal space 6c increases, so that excess oil in the frame internal space 6c can be discharged out of the frame 6 through the oil discharge holes 6b. Therefore, even if the rotation speed of the main shaft 14 increases and the amount of oil pumped up by the oil pump 17 increases, it is possible to prevent an excessive increase in the hydraulic pressure in the frame inner space 6c.
  • the opening characteristic of the oil discharge valve 28 can be arbitrarily adjusted by the rigidity of the leaf spring portion of the oil discharge valve 28 and the initial deformation amount. Since the oil drain valve 28 is provided in the oil drain hole 6b of the frame 6 fixed to the sealed container 60, the oil drain valve 28 is different from the configuration in which the oil drain valve is provided in a rotating part such as a main shaft. Centrifugal force does not act on. Thereby, it is not necessary to consider the centrifugal force as a load acting on the oil discharge valve 28, and for example, only the oil pressure P needs to be considered. Therefore, the opening characteristic of the oil discharge valve 28 can be easily adjusted. Further, it is possible to prevent the opening characteristic of the oil discharge valve 28 from changing depending on the rotation speed of the main shaft 14. Furthermore, since centrifugal force does not act on the oil discharge valve 28, the strength and reliability of the oil discharge valve 28 can be ensured. Therefore, according to the present embodiment, excess oil in the frame inner space 6c can be discharged out of the frame 6 appropriately.
  • the oil drain hole 6b is provided fixed to the sealed container 60, it is possible to prevent the oil from being scattered as compared with the configuration in which the oil is discharged from the outer peripheral surface of the rotating main shaft. Therefore, it is possible to suppress the oil from being wound up by the refrigerant, and it is possible to suppress an increase in the oil.
  • the scroll fluid machine according to the present embodiment is characterized in that the oil discharge valve 28 has a reed valve structure that is opened and closed by the hydraulic pressure P. According to this configuration, the configuration of the oil discharge valve 28 can be simplified.
  • the scroll fluid machine is attached to the outside of the frame 6 and receives an oil receiver 27 that receives oil discharged from the oil drain hole 6b, an oil receiver 27, and an oil sump 18 at the bottom of the sealed container 60. And an oil drain pipe 8b for returning the oil received by the oil receiver 27 to the oil sump 18 at the bottom of the sealed container 60.
  • the oil discharged from the oil discharge hole 6b can be returned to the oil sump 18 without being exposed to the flow of the fluid (refrigerant) in the sealed container 60, thereby further suppressing an increase in oil rise. Can do.
  • FIG. 5 is an enlarged sectional view showing a part of the scroll compressor according to the present embodiment.
  • symbol is attached
  • the oil drain valve 28 of the present embodiment includes a valve body 28a and a coil spring 28b that biases the valve body 28a.
  • the oil drain hole 6b is provided on the frame inner space 6c side (upstream side) and extends in the horizontal direction, and is provided on the oil receiver 27 side (downstream side). And a downstream portion 6e.
  • the valve body 28a is provided between the upstream portion 6d and the downstream portion 6e of the oil discharge hole 6b.
  • the valve body 28a is provided so as to be slidable in the horizontal direction coaxial with the upstream portion 6d.
  • the valve body 28a takes at least a closed position for closing the oil drain hole 6b and an open position for opening the oil drain hole 6b.
  • the opening degree of the oil drain hole 6b depends on the position of the valve body 28a. Is changing.
  • the upstream portion 6d is provided with a stopper 32 that regulates the closed position (initial position) of the valve body 28a.
  • the coil spring 28b biases the valve body 28a in the direction from the open position to the closed position.
  • the coil spring 28b is contracted and deformed by a predetermined contraction amount when the valve element 28a is in the closed position.
  • a hydraulic pressure P of the frame inner space 6c acts on the valve body 28a in a direction from the closed position toward the open position (counter biasing direction).
  • the biasing force of the coil spring 28b is adjusted so that the valve element 28a starts to slide in the counter-biasing direction when the hydraulic pressure P in the frame inner space 6c increases to reach a predetermined pressure P ′. .
  • valve body 28a When the valve body 28a is in the closed position, the upstream portion 6d and the downstream portion 6e are closed by the valve body 28a, and the oil drain valve 28 is in a closed state.
  • the hydraulic pressure P in the frame inner space 6c increases to reach the pressure P ′, the hydraulic pressure P acting on the valve body 28a overcomes the urging force of the coil spring 28b, and the valve body 28a slides in the direction from the closed position toward the open position. Start moving. As a result, the upstream portion 6d and the downstream portion 6e communicate with each other, and the oil drain valve 28 is opened.
  • the hydraulic pressure P increases, the amount of contraction of the coil spring 28b increases, and the opening degree of the oil discharge valve 28 increases.
  • FIG. 6 is an enlarged cross-sectional view showing a part of a scroll compressor according to a modification of the present embodiment.
  • the moving direction of the valve element 28a of the oil discharge valve 28 is horizontal, but the moving direction of the valve element 28a may be vertical as in the configuration shown in FIG. .
  • the upper surface of the valve body 28a is inclined toward the frame internal space 6c so that the hydraulic pressure P is likely to act on the valve body 28a from the closed position toward the open position. Also good.
  • the oil discharge valve 28 has the valve body 28a and the coil spring 28b, and the valve body 28a is closed to close the oil discharge hole 6b.
  • the coil spring 28b urges the valve body 28a in the direction from the open position to the closed position, and takes the valve body 28a. Is characterized in that the hydraulic pressure P acts in the direction from the closed position toward the open position.
  • FIG. 7 is an enlarged cross-sectional view of a part of the scroll compressor according to the present embodiment.
  • symbol is attached
  • the oil drain valve 28 of the present embodiment has a valve body 28a that is slidable in the vertical direction.
  • the oil drain hole 6b extends in the horizontal direction as a whole, and has an upstream portion 6d provided on the frame internal space 6c side and a downstream portion 6e provided on the oil receiver 27 side.
  • the valve body 28a is provided between the upstream portion 6d and the downstream portion 6e of the oil discharge hole 6b.
  • a vertical hole 28c is formed above the valve body 28a so that the valve body 28a can be slid in the vertical direction (for example, the vertical vertical direction).
  • the valve body 28a has at least a lower closed position for closing the oil drain hole 6b and an upper open position for opening the oil drain hole 6b.
  • the oil drain hole depends on the position of the valve body 28a.
  • the opening degree of 6b changes.
  • the space in the vertical hole 28 c and the outside of the frame 6 communicate with each other through a pressure equalizing hole 33.
  • the pressure P 0 in the space in the vertical hole 28 c is equalized with the pressure outside the frame 6 (for example, the suction space in the sealed container 60).
  • a downward force (F + P 0 ⁇ A) from the open position to the closed position is applied to the valve body 28a by its own weight F and the pressure P 0 acting on the upper surface.
  • an upward force (P ⁇ A) from the closed position to the open position is applied to the valve body 28a by the hydraulic pressure P of the frame internal space 6c acting on the lower surface.
  • the hydraulic pressure P in the frame inner space 6c is low, the downward force is greater than the upward force, and thus the valve body 28a is located at the lower closed position. In this state, the upstream portion 6d and the downstream portion 6e are closed by the valve body 28a, and the oil drain valve 28 is closed.
  • the oil drain valve 28 has the valve body 28a, and the valve body 28a has a closed position in which the oil drain hole 6b is closed, and a closed position. And at least an open position that opens the oil drain hole 6b.
  • Gravity acts on the valve body 28a in a direction from the open position toward the closed position, and from the closed position.
  • the hydraulic pressure P acts in the direction toward the open position.
  • FIG. 8 is an enlarged cross-sectional view of a part of the scroll compressor according to the present embodiment.
  • symbol is attached
  • this embodiment is characterized in that the oil drain hole 6a (and the oil drain pipe 8a) that is always open is not provided.
  • the surplus portion of the oil stored in the frame internal space 6c is discharged out of the frame 6 only from the oil drain hole 6b provided with the oil drain valve 28.
  • the oil discharged from the oil drain hole 6b is received by the oil receiver 27 and returns to the oil sump 18 through the oil drain pipe 8b.
  • the oil discharge valve 28 of this example has a reed valve structure similar to that of the first embodiment, but may have a configuration similar to that of the second or third embodiment. Further, a plurality of oil drain holes 6b may be provided, and the oil drain valve 28 may be provided in all of the plurality of oil drain holes 6b.
  • FIG. 9 is an enlarged cross-sectional view of a part of the scroll compressor according to the present embodiment.
  • symbol is attached
  • an oil drain hole 6b provided with an oil drain valve 28 and an oil drain hole 6a that is always open are provided and discharged from the oil drain hole 6b.
  • the oil receiver 27 receives not only the oil but also the oil discharged from the oil drain hole 6a. The oil received by the oil receiver 27 returns to the oil sump 18 through the oil drain pipe 8b.
  • a plurality of oil drain holes 6a that are always open may be provided.
  • the present invention is not limited to the above embodiment, and various modifications can be made.
  • the scroll compressor is taken as an example of the scroll fluid machine, but the present invention can also be applied to other scroll fluid machines such as a scroll pump.

Landscapes

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

Abstract

L'invention porte sur une machine à fluide à volutes, laquelle machine est caractérisée en ce qu'elle a : une volute stationnaire (4) et une volute orbitante (5), qui sont situées à l'intérieur d'un récipient hermétique (60) ; un bâti (6) pour porter la volute orbitante (5) de telle sorte que la volute orbitante peut orbiter ; un espace (6c) à l'intérieur du bâti, l'espace (6c) étant formé entre le bâti (6) et la volute orbitante (5) ; un arbre principal (14) pour transmettre une puissance d'entraînement à la volute orbitante (5) ; un trou d'évacuation d'huile (6b) formé de façon à s'étendre à travers le bâti (6) et à évacuer un excès d'huile présent à l'intérieur de l'espace (6c) à l'intérieur du bâti vers l'extérieur du bâti (6) ; et une soupape d'évacuation d'huile (28) située sur le trou d'évacuation d'huile (6b) et ouvrant et fermant le trou d'évacuation d'huile (6b) en fonction de la pression d'huile (P) à l'intérieur de l'espace (6c) à l'intérieur du bâti.
PCT/JP2013/079033 2013-10-25 2013-10-25 Machine à fluide à volutes WO2015059833A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2015543680A JP6120982B2 (ja) 2013-10-25 2013-10-25 スクロール流体機械
PCT/JP2013/079033 WO2015059833A1 (fr) 2013-10-25 2013-10-25 Machine à fluide à volutes

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2013/079033 WO2015059833A1 (fr) 2013-10-25 2013-10-25 Machine à fluide à volutes

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WO2015059833A1 true WO2015059833A1 (fr) 2015-04-30

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JP (1) JP6120982B2 (fr)
WO (1) WO2015059833A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018220747A1 (fr) * 2017-05-31 2018-12-06 三菱電機株式会社 Compresseur à spirale et appareil à cycle de réfrigération
WO2023181141A1 (fr) * 2022-03-23 2023-09-28 三菱電機株式会社 Compresseur à spirale horizontale et appareil à cycle de réfrigération équipé dudit compresseur à spirale horizontale

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58160583A (ja) * 1982-03-19 1983-09-24 Hitachi Ltd スクロ−ル式流体機械
JP2001336485A (ja) * 2000-05-29 2001-12-07 Mitsubishi Electric Corp スクロール圧縮機
JP2003214364A (ja) * 2001-11-13 2003-07-30 Mitsubishi Electric Corp スクロール圧縮機
JP2009270433A (ja) * 2008-04-30 2009-11-19 Hitachi Appliances Inc スクロール圧縮機
JP2010106780A (ja) * 2008-10-31 2010-05-13 Hitachi Appliances Inc スクロール圧縮機
JP2010138758A (ja) * 2008-12-10 2010-06-24 Hitachi Appliances Inc スクロール圧縮機
WO2012039109A1 (fr) * 2010-09-21 2012-03-29 株式会社ヴァレオジャパン Compresseur à volute
JP2013204476A (ja) * 2012-03-28 2013-10-07 Hitachi Appliances Inc スクロール圧縮機

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58160583A (ja) * 1982-03-19 1983-09-24 Hitachi Ltd スクロ−ル式流体機械
JP2001336485A (ja) * 2000-05-29 2001-12-07 Mitsubishi Electric Corp スクロール圧縮機
JP2003214364A (ja) * 2001-11-13 2003-07-30 Mitsubishi Electric Corp スクロール圧縮機
JP2009270433A (ja) * 2008-04-30 2009-11-19 Hitachi Appliances Inc スクロール圧縮機
JP2010106780A (ja) * 2008-10-31 2010-05-13 Hitachi Appliances Inc スクロール圧縮機
JP2010138758A (ja) * 2008-12-10 2010-06-24 Hitachi Appliances Inc スクロール圧縮機
WO2012039109A1 (fr) * 2010-09-21 2012-03-29 株式会社ヴァレオジャパン Compresseur à volute
JP2013204476A (ja) * 2012-03-28 2013-10-07 Hitachi Appliances Inc スクロール圧縮機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018220747A1 (fr) * 2017-05-31 2018-12-06 三菱電機株式会社 Compresseur à spirale et appareil à cycle de réfrigération
WO2023181141A1 (fr) * 2022-03-23 2023-09-28 三菱電機株式会社 Compresseur à spirale horizontale et appareil à cycle de réfrigération équipé dudit compresseur à spirale horizontale

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JP6120982B2 (ja) 2017-04-26

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