WO2015182214A1 - Compresseur - Google Patents

Compresseur Download PDF

Info

Publication number
WO2015182214A1
WO2015182214A1 PCT/JP2015/057315 JP2015057315W WO2015182214A1 WO 2015182214 A1 WO2015182214 A1 WO 2015182214A1 JP 2015057315 W JP2015057315 W JP 2015057315W WO 2015182214 A1 WO2015182214 A1 WO 2015182214A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
bypass
main shaft
hole
slide member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2015/057315
Other languages
English (en)
Japanese (ja)
Inventor
英彰 永田
下地　美保子
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2016523187A priority Critical patent/JP6180630B2/ja
Publication of WO2015182214A1 publication Critical patent/WO2015182214A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

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
    • 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

  • the present invention relates to a compressor used in, for example, a refrigeration air conditioner.
  • Patent Document 1 a scroll compressor that prevents excessive supply of oil to the compression mechanism, reduces oil consumption, and improves the volumetric efficiency of the compressor.
  • Patent Document 1 a main shaft in which an oil hole extending in the axial direction and a bypass hole for discharging oil passing through the oil hole to the outside of the main shaft are formed, and a centrifuge that is provided on the bypass hole and is generated by the rotational motion of the main shaft.
  • a scroll compressor including a slide valve that opens and closes a bypass hole by force is disclosed.
  • JP 2000-213480 (paragraph 0026-0029, FIG. 4)
  • the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a compressor capable of accurately adjusting the amount of oil discharged from the bypass hole.
  • a compressor of the present invention is a compressor including a sealed container that stores oil in a lower part and a compression mechanism that is housed in the sealed container and compresses a working fluid, and is connected to the compression mechanism, An oil passage that extends in the axial direction through which the stored oil passes and a main shaft that is formed with a discharge hole that discharges oil passing through the oil passage, and oil that is attached to the main shaft and stored in a sealed container is supplied to the oil passage.
  • An oil pump and a bypass device that is fixed on the discharge hole of the main shaft and adjusts the amount of oil discharged from the discharge hole.
  • the bypass device has one side fixed on the main shaft discharge hole and the other side opened.
  • a housing in which a hollow part into which oil flows from the discharge hole and a bypass hole through which oil flows into the hollow part is formed, and is accommodated in the hollow part so as to be movable in the radial direction, and moves on the bypass hole.
  • a biasing member that is accommodated in the hollow portion and biases the slide member from the other side of the housing to the one side, and a fixed lid that is attached to the opening on the other side of the hollow portion of the housing and seals the hollow portion
  • the slide member is configured to partition the hollow portion into a first space on the main shaft side and a second space on the bias member side when the main shaft rotates in the radial direction due to centrifugal force when the main shaft rotates.
  • a pressure equalizing path connecting the first space and the second space is formed in the hollow portion of the housing.
  • the compressor of the present invention by providing a pressure equalization path that connects the first space and the second space of the hollow portion, the position of the slide member is not affected by the oil pressure applied from the main shaft side, and the main shaft rotates. Since it is determined according to the number, the amount of oil discharged from the discharge hole can be adjusted with high accuracy.
  • FIG. 3 is a cross-sectional view showing an AA cross section in the bypass device of FIG. 2.
  • FIG. 6 is a cross-sectional view showing another example of the AA cross section in the bypass device of FIG. 2.
  • It is a schematic diagram which shows the operation example of the bypass apparatus of FIG. It is a schematic diagram which shows the operation example of the bypass apparatus of FIG. It is a graph which shows the relationship between the rotation speed in the compressor of FIG.
  • FIG. 1 is a schematic longitudinal sectional view of a compressor according to Embodiment 1 of the present invention.
  • a compressor 1 in FIG. 1 is a so-called vertical scroll compressor, and compresses and discharges a working gas such as a refrigerant in a scroll-like compression chamber, for example.
  • the compressor 1 includes a sealed container 2, a main shaft 5, an oil pump 7, a motor 8, and a compression mechanism 10.
  • the sealed container 2 is formed in a cylindrical shape, for example, and has pressure resistance.
  • a suction pipe 2A for taking the working gas into the sealed container 2 is connected to the side surface of the sealed container 2, and a discharge pipe 2B for discharging the compressed working gas from the sealed container 2 is connected to the upper surface.
  • a frame 3 is fixed to the upper side of the sealed container 2, and a sub-frame 4 that holds the main shaft 5 is fixed to the lower side.
  • An oil sump 2 ⁇ / b> C for storing lubricating oil is formed at the bottom of the sealed container 2.
  • the main shaft 5 is rotatably supported by the frame 3 and the subframe 4 in the sealed container 2.
  • An upper portion of the main shaft 5 is rotatably supported on the frame 3 by a main bearing 3a such as a bearing, and a lower portion of the main shaft 5 is rotatably supported on the sub frame 4 by a sub bearing 4a such as a bearing.
  • an eccentric shaft portion 6 is attached to the upper end of the main shaft 5 in an eccentric state with respect to the main shaft 5.
  • an oil passage 5a through which oil flows is formed in the main shaft 5, and oil is supplied to each sliding portion such as the main bearing 3a and the sub bearing 4a through the oil passage 5a.
  • the oil pump 7 is attached to the lower end of the main shaft 5, and supplies oil stored in the oil sump 2 ⁇ / b> C of the sealed container 2 to the oil passage 5 a in the main shaft 5.
  • the oil pump 7 is composed of, for example, a rotary positive displacement pump.
  • the oil pump 7 operates as the main shaft 5 rotates, and the amount of oil supplied to the oil passage 5a increases as the rotation speed of the main shaft 5 increases. It has characteristics.
  • the motor 8 rotates the main shaft 5 and has a motor rotor 8A and a motor stator 8B.
  • the motor stator 8B is fixed to the sealed container 2, and the motor rotor 8A is fixed to the main shaft 5.
  • the main shaft 5 and the motor rotor 8A rotate with respect to the motor stator 8B.
  • the compression mechanism 10 compresses and discharges working gas such as refrigerant, and includes a swing scroll 11 and a fixed scroll 12.
  • the swing scroll 11 is supported by the frame 3 so as to be capable of revolving, and a cylindrical swing bearing 11 a is provided on the lower surface of the swing scroll 11.
  • the eccentric shaft portion 6 of the main shaft 5 is inserted into the rocking bearing 11 a, and the rocking scroll 11 performs a revolving motion by the rotation of the eccentric shaft portion 6.
  • An Oldham ring (not shown) is supported between the frame 3 and the orbiting scroll 11 so as to be swingable on the frame 3 in order to give a swinging motion while preventing the swinging scroll 11 from rotating. Is provided.
  • a slider 9 is provided between the main shaft 5 and the orbiting scroll 11, and the slider 9 has a direction in which the oscillation radius increases due to the force of the working gas and the centrifugal force acting on the orbiting scroll 11.
  • a variable crank mechanism for converting the rotation of the main shaft 5 into a revolving motion.
  • the fixed scroll 12 is arranged on the top of the swing scroll 11 and is fixed to the frame 3.
  • a discharge port 12a for discharging the working gas is formed at the center of the fixed scroll 12, and a check valve 14 for preventing a back flow of the compressed working gas is disposed on the discharge port 12a.
  • the check valve 14 has a movable range restricted by a valve presser 15, and the check valve 14 and the valve presser 15 are fixed to the fixed scroll 12 by a valve bolt 16.
  • a spiral body is formed on each of the upper surface of the swing scroll 11 and the lower surface of the fixed scroll 12, and the swing scroll 11 and the fixed scroll 12 are disposed so that the spiral bodies face each other.
  • a compression chamber is formed between the spiral portion of the fixed scroll 12 and the spiral portion of the orbiting scroll 11.
  • the compressor 1 has an oil return pipe 20 that connects the frame 3 and the lower part of the sealed container 2.
  • oil return pipe 20 oil flowing in a space (space in the frame) formed by the frame 3 and the swing scroll 11 flows toward the lower part of the sealed container 2.
  • the main shaft 5 is also provided with a first balancer 21 and a second balancer 22 that cancel out the imbalance caused by the orbiting scroll 11 and the slider 9.
  • the main shaft 5 rotates in the arrow R direction.
  • the eccentric shaft portion 6 is rotated by the rotation of the main shaft 5, and the swing scroll 11 performs swing motion (revolution motion).
  • the working gas is compressed in a compression chamber formed between the swing scroll 11 and the fixed scroll 12.
  • the working gas is taken into the sealed container 2 from the suction pipe 18, passes through a port (not shown) provided in the frame 3, and is taken into the compression chamber.
  • the compressed working gas pushes up the check valve 14 and is discharged from the discharge port 12a of the fixed scroll 12 into the space between the sealed containers 2, and then passes through the discharge pipe 2B and is discharged to the outside of the compressor 1. Is done.
  • the oil pump 7 operates to supply oil to the oil passage 5 a of the main shaft 5.
  • This oil passes from the oil passage 5 a to the sub bearing 4 a between the sub frame 4 and the main shaft 5, the main bearing 3 a between the frame 3 and the main shaft 5, and the rocking bearing 11 a between the rocking scroll 11 and the slider 9.
  • Each is refueled.
  • the oil supplied to the sub-bearing 4a lubricates the sub-bearing 4a and then returns to the lower part of the sealed container 2.
  • the oil supplied to the main bearing 3a lubricates the main bearing 3a, and then branches into a lower part and an upper part of the frame 3.
  • the oil that has flowed to the lower portion passes through a gap between the motor rotor 8A and the motor stator 8B and a passage (not shown) provided in the motor stator 8B, and is returned to the lower portion of the hermetic container 2.
  • the oil that has flowed to the top and the oil after lubricating the rocking bearing 11a flows into the space formed by the rocking scroll 11 and the frame 3 (the space in the frame 3), and most of the oil is returned to the oil. It passes through the tube 20 and is returned to the lower part of the sealed container 2.
  • the remaining part of the oil passes between the thrust surface of the orbiting scroll 11 and the frame 3, is taken into the compression chamber, and is then discharged to the outside of the compressor 1.
  • the oil in the frame is agitated by the rocking bearing 11 a of the rocking scroll 11.
  • the oil pump 7 is, for example, a rotary positive displacement pump, and the amount of oil supplied to the oil passage 5a increases as the rotational speed of the main shaft 5 increases. Therefore, the amount of oil supply becomes excessive when the compressor 1 rotates at a high speed, and as the amount of oil discharged to the outside of the compressor 1, that is, the amount of oil rising increases, the refrigerating capacity and performance may decrease. Therefore, the compressor 1 of FIG. 1 is provided with a bypass device 30 that discharges the oil passing through the oil passage 5a on the way and adjusts the supply amount of the oil.
  • FIG. 2 is a schematic cross-sectional view of the bypass device in the compressor of FIG. 1
  • FIG. 3 is a schematic view showing an example of a bypass hole of the bypass device of FIG. 2, and the bypass device 30 will be described with reference to FIGS. explain.
  • the main shaft 5 is formed with a discharge hole 5b for discharging oil from the oil passage 5a, for example, below the second balancer 22, and the bypass device 30 is fixed on the discharge hole 5b of the main shaft 5.
  • the bypass device 30 includes a housing 31, a slide member 40, and an urging member 41.
  • the housing 31 includes a holder 32 having a hollow portion 36 having one side 31x fixed to the main shaft 5 and the other side 31y closed by a fixing lid 33.
  • the holder 32 is formed in a disk shape, for example, and a hollow portion 36 extending in the radial direction (the arrow X direction in FIGS. 2 and 3) is formed in a part of the holder 32.
  • the hollow portion 36 has a shape in which one side 31x is fixed to the main shaft 5 and the other side 31y is opened.
  • An oil outlet 35 leading to the discharge hole 5b is formed on one side 31x, and a fixed lid 33 is attached to the other side 31y so as to seal the inside of the holder 32. Therefore, the oil passing through the oil passage 5 a from the discharge hole 5 b flows into the hollow portion 36 from the oil outlet 35.
  • the fixed lid 33 prevents oil having a pressure higher than the pressure of the sealed container 2 in the holder 32 from being discharged to the sealed container 2 from other than the bypass hole 37.
  • the slide member 40 is accommodated in the hollow portion 36 so as to be movable in the radial direction (arrow X direction in FIGS. 2 and 3), and functions as a valve that moves on the bypass hole 37 and adjusts the opening degree of the bypass hole 37. To do. Specifically, the slide member 40 is positioned on the bypass hole 37 in the initial state, and is in a state of closing the bypass hole 37. When the main shaft 5 rotates, the slide member 40 moves to the other side 31y (outside) of the hollow portion 36 by centrifugal force, and the opening area of the bypass hole 37 changes depending on the position of the slide member 40. Yes.
  • the urging member 41 is made of, for example, a coil spring and is accommodated in the hollow portion 36 in a state of being attached to the fixed lid 33.
  • the biasing member 41 biases the slide member 40 from the other side 31y of the housing 31 to the one side 31x when the main shaft 5 rotates.
  • FIG. 2 for example, the case where the slide member 40 is positioned at a position closing the oil outlet 35 and the bypass hole 37 in the state where the urging member 41 is in a natural length is illustrated.
  • the slide member 40 moves in the radial direction (in the direction of the arrow X1 in FIG. 2) by centrifugal force, and the hollow portion 36 is moved between the first space 36A on the main shaft 5 side and the biasing member 41 side. Partitioning into the second space 36B (see FIGS. 3 and 6).
  • a pressure equalizing path 38 that connects the first space 36A and the second space 36B is formed in the hollow portion 36 of the housing 31.
  • 4 is a cross-sectional view showing an AA cross section of the bypass device of FIG. As shown in FIG. 4, the pressure equalization path 38 is formed by a gap formed between the inner surface of the housing 31 (holder 32) and the outer surface of the slide member 40. This gap is caused by the difference between the outer diameter of the slide member 40 and the inner diameter of the holder 32.
  • the gap is not a narrow gap that keeps the sliding portion airtight with lubricating oil, but is preferably somewhat wider than such a narrow gap, for example, about 0.025 to 0.1 mm. If the gap is smaller than 0.025 mm, the oil cannot flow quickly through the gap, and the influence of the pressure change in the second space 36B and the pressure change from the main shaft 5 when the slide member 40 moves increases. If the gap is larger than 0.1 mm, even if the slide member 40 closes the bypass hole 37, more oil flows out of the bypass hole 37 through the gap. In FIG. 2, a gap is also formed at a portion of the slide member 40 that closes the oil outlet 35 to form a pressure equalizing path 38. Such a gap can be produced by forming fine irregularities and grooves on the surface of the slide member 40 or the surface on which the oil outlet 35 is formed.
  • FIG. 5 is a cross-sectional view showing another example of the AA cross section in the bypass device of FIG.
  • the pressure equalization path 38 is formed by a gap between the inner surface of the holder 32 and the outer surface of the slide member 40 and a groove provided at a position different from the bypass hole 37 on the holder 32 side. ing.
  • the slide member 40 between the first space 36 ⁇ / b> A and the second space 36 ⁇ / b> B even when the oil pressure on the first space 36 ⁇ / b> A side changes suddenly.
  • the pressure equalization can be reliably performed.
  • channel is provided in the holder 32 side, you may make it provide a groove
  • a groove communicating from the oil outlet 35 may be formed in a portion of the slide member 40 that closes the oil outlet 35.
  • the operation of the bypass device 30 during the operation of the compressor 1 will be described with reference to FIGS.
  • the main shaft 5 rotates in the arrow R direction.
  • the bypass device 30 rotates in the arrow R direction along with the rotation of the main shaft 5.
  • a centrifugal force acting radially outward acts on the slide member 40, and the slide member 40 radially outwards in the hollow portion 36 of the housing 31 (in the direction of arrow X1 in FIG. 2). Move towards.
  • the oil flowing into the hollow portion 36 flows from the first space 36A side through the pressure equalization path 38 to the second space 36B side.
  • the front surface and the rear surface of the slide member 40 have substantially the same pressure (equal pressure). Therefore, the position of the slide member 40 is not affected by the oil pressure, and the position of the slide member 40 is determined by the centrifugal force of the slide member 40 and the elastic force of the biasing member 41.
  • the centrifugal force Fcf acting on the slide member 40 is expressed by the following formula (1).
  • m is the mass of the slide member 40
  • r is the distance in the radial direction (arrow X direction) from the center of the main shaft 5 to the center of gravity of the slide member 40
  • ⁇ is the angular velocity of the main shaft 5.
  • a force in the direction opposite to the centrifugal force Fcf from the urging member 41 to the main shaft 5 acts on the slide member 40.
  • the force acting from the urging member 41 is represented by the following formula (2).
  • Equation (1) k is a spring constant of the urging member 41, x is a deformation amount of the urging member 41, and is a moving distance of the slide member 40 in the radial direction (arrow X direction).
  • the position of the slide member 40 is determined under a condition in which the centrifugal force Fcf acting on the slide member 40 of Expression (1) and the force Fs acting on the biasing member 41 of Expression (2) are balanced.
  • the position of the slide member 40 is determined by the rotational speed ⁇ of the main shaft 5 without depending on the oil pressure of the oil flowing from the discharge hole 5b to the first space 36A.
  • the rotational speed ⁇ of the main shaft 5 at which oil draining is started can be arbitrarily adjusted.
  • the rotational speed ⁇ of the main shaft 5 at which oil drainage is started is arbitrarily set. Can be adjusted.
  • the oil drainage characteristic of the bypass device 30 can be arbitrarily set by the formation position of the bypass hole 37 and the size of the opening. For example, as the position where the bypass hole 37 is formed is closer to the main shaft 5, the rotational speed ⁇ at which drainage is started becomes smaller, and as the position where the bypass hole 37 is formed is farther from the main shaft 5, the rotational speed ⁇ 1 is started. Becomes bigger. Further, the smaller the opening of the bypass hole 37, the smaller the amount of oil drained, and the larger the opening of the bypass hole 37, the larger the amount of oil discharged.
  • FIG. 6 and 7 are schematic diagrams showing an operation example of the bypass device 30 of FIG. 2, and FIG. 8 is a graph showing the relationship between the rotational speed and the amount of oil supplied from the oil passage in the compressor of FIG.
  • FIG. 8 is a graph showing the relationship between the rotational speed and the amount of oil supplied from the oil passage in the compressor of FIG.
  • the period until the rotational speed ⁇ reaches the predetermined rotational speed ⁇ 1 is a period in which the slide member 40 is positioned on the bypass hole 37, and the bypass hole 37 does not communicate with the oil passage 5 a and is discharged from the bypass device 30. No oil is done. Accordingly, everything except the amount of oil supplied to the auxiliary bearing 4a by the oil pump 7 is supplied to the rocking bearing 11a and the main bearing 3a.
  • the first space 36A and the second space 36B in the hollow portion 36 communicate with each other through the pressure equalization path 38, so that the inside of the hollow portion 36
  • the position of the slide member 40 is determined by the rotational speed ⁇ without depending on the oil pressure.
  • the opening area of the bypass hole 37 can be accurately controlled by the rotational speed ⁇ , the oil can be supplied to each sliding portion without excess or deficiency according to the driving situation.
  • less oil is stirred in the space in the frame 3 and stirring loss is reduced.
  • the amount of oil passing between the thrust surface of the orbiting scroll 11 and the frame 3 is reduced, and the amount of oil discharged to the outside of the compressor 1 is also reduced, so that the amount of oil rising can be suppressed.
  • the oil discharge amount may vary depending on the state of the oil such as viscosity, for example, and it is difficult to adjust the oil discharge amount and the oil supply amount according to the rotational speed.
  • the pressure equalizing path 38 is provided as in the bypass device 30 of FIG. 2, the oil pressure applied to the main shaft 5 side of the slide member 40 and the oil pressure applied to the biasing member 41 side are the same. Therefore, since the opening area of the bypass hole 37 can be accurately controlled by the rotational speed ⁇ without depending on the oil pressure, the oil can be supplied to each sliding portion without excess or deficiency in accordance with the rotational speed ⁇ . .
  • FIG. FIG. 9 is a schematic diagram showing Embodiment 2 of the bypass device in the compressor of the present invention.
  • the bypass device will be described with reference to FIG. 9, parts having the same configuration as the bypass device 30 in FIG. 2 are denoted by the same reference numerals and description thereof is omitted. 9 differs from the bypass device 30 of FIG. 2 in the structure of the pressure equalization path 138.
  • the pressure equalizing path 138 is formed by a through hole provided in the slide member 40.
  • the opening area of the pressure equalization path 138 can be increased, even if the oil pressure changes rapidly, the oil pressure in the first space 36A and the second space 36B of the hollow portion 36 is substantially the same. Can be. Therefore, the opening area of the bypass hole 37 can be accurately controlled by the rotational speed ⁇ without depending on the oil pressure.
  • the slide member 40 blocks the bypass hole 37. In addition, it is possible to reduce the spilled oil.
  • FIG. 9 illustrates the case where the pressure equalizing path 138 is formed by a through hole provided in the slide member 40, it is formed from both the gap (see FIG. 2) and the above-described through hole. It may be.
  • FIG. 10 to 14 are schematic views showing bypass holes of the bypass device according to Embodiment 3 of the compressor of the present invention.
  • the bypass devices 230A to 230E will be described with reference to FIGS. 10 to FIG. 14, parts having the same configuration as the bypass device 30 of FIG. 3 are denoted by the same reference numerals and description thereof is omitted.
  • the bypass devices 230A to 230E shown in FIGS. 10 to 14 are different from the bypass device 30 shown in FIG. 3 in the shape and structure of the discharge holes.
  • the housing 231 is provided with two bypass holes 237a and 237b made of circular holes.
  • the two bypass holes 237a and 237b are arranged in the radial direction (arrow X direction) is illustrated, they may be arranged side by side in the circumferential direction.
  • the housing 231 is provided with three bypass holes 237c, 237d, and 237e formed of circular holes.
  • the present invention is not limited thereto, and four or more may be provided.
  • bypass hole 237f made of an elliptical hole is provided in the bypass device 230C of FIG. 12.
  • one bypass hole 237g made of a rectangular hole is provided in the bypass device 230D of FIG. 13
  • one bypass hole 237h made of a triangular hole is provided in the bypass device 230E of FIG. 14. It may be polygonal. Furthermore, a plurality of discharge holes of these shapes may be provided as shown in FIGS.
  • FIG. 15 is a graph showing the relationship between the rotational speed and the amount of oil supply in the compressor using the bypass device of FIGS.
  • the oil discharge amount OC increases as the rotational speed ⁇ increases, and the oil supply amount becomes constant. Thereby, the amount of oil rising at the time of high rotation can be suppressed reliably.
  • FIG. FIG. 16 is a schematic diagram showing Embodiment 4 of the bypass device in the compressor of the present invention.
  • the bypass device will be described with reference to FIG. In the bypass device of FIG. 16, parts having the same configuration as the bypass device of FIG. 2 are denoted by the same reference numerals and description thereof is omitted.
  • the bypass device 330 of FIG. 16 differs from the bypass device 30 of FIG. 2 in that the bypass device 330 functions as a second balancer.
  • the bypass device 330 has a function as a balancer, and the housing 31 has a shape in which the length of the radius is different in the circumferential direction.
  • the bypass device 330 cancels the imbalance caused by the orbiting scroll 11 and the slider 9 instead of the second balancer 22 in FIG.
  • the bypass device 30 can be provided in the compressor 1 with a small number of parts, and the cost and size can be reduced. Even in this case, similarly to the first embodiment, the opening area of the bypass hole 37 can be accurately controlled by the rotational speed ⁇ without depending on the oil pressure.
  • FIG. 17 and 18 are schematic views showing Embodiment 5 of the bypass device in the compressor of the present invention.
  • the bypass device will be described with reference to FIGS. 17 and 18. 17 and 18, parts having the same configuration as the bypass device of FIG. 2 are denoted by the same reference numerals and description thereof is omitted.
  • the bypass device 430 of FIGS. 17 and 18 is different from the bypass device 30 of FIG. 2 in the structure of pressure equalization paths 431 and 432.
  • the pressure equalization path 431 is also in communication with the first space 36A via the oil outlet 35, and substantially connects the first space 36A and the second space 36B.
  • the pressure equalization path 432 in FIG. 18 is formed inside the holder 32, and is a path that connects the discharge hole 5b and the second space 36B. In this case as well, the pressure equalizing path 431 is in communication with the first space 36A via the discharge hole 5b and the oil outlet 35, and substantially connects the first space 36A and the second space 36B. It has become. 17 and 18, as in the case of FIG. 5 described above, the difference between the outer diameter of the slide member 40 and the inner diameter of the holder 32 is made smaller than in the case of FIG. The oil that flows out may be reduced when the oil is blocked.
  • the opening area of the bypass hole 37 can be accurately controlled by the rotational speed ⁇ without depending on the oil pressure. Oil can be supplied to each sliding part without excess or deficiency.
  • FIG. FIG. 19 is a schematic diagram showing Embodiment 6 of the bypass device in the compressor of the present invention.
  • the bypass device will be described with reference to FIG. In the bypass device of FIG. 19, parts having the same configuration as the bypass device of FIG.
  • the bypass device 530 in FIG. 19 is different from the bypass device 30 in FIG. 2 in that a protrusion 531 is provided at the outlet of the bypass hole 37.
  • the housing 31 has a protruding portion 531 protruding from the lower end surface of the holder 32 at the outlet of the bypass hole 37. Then, when the bypass device 30 rotates, a large negative pressure is generated as compared with the case where the bypass hole 37 is not projected near the outlet of the bypass hole 37. By generating a large negative pressure, the bypass hole 37 can be reduced, and the size of the holder 32 can be reduced. That is, the cost and size of the bypass device 30 can be reduced. Even in the present embodiment, since the negative pressure generated at the outlet of the bypass hole 37 changes depending on the rotational speed ⁇ , the bypass hole 37 does not depend on the oil pressure as in the first embodiment. The opening area can be accurately controlled by the rotational speed ⁇ .
  • FIG. 1 illustrates the case where the compressor 1 is a scroll compressor, for example, a vane type compressor or a rotary type compressor may be used.
  • a so-called vertical compressor is illustrated in FIG. 1, it can also be applied to a horizontal compressor.
  • the fixed lid 33 is provided on the other side 31y of the hollow portion 36 is illustrated, the holder 32 and the fixed lid 33 may be integrally formed.
  • the oil is discharged according to the rotational speed ⁇ . If it adjusts, it will not be limited to the said height position, What is necessary is just to be provided in the upstream of the oil path 5a.

Landscapes

  • 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 concerne un compresseur pourvu d'un dispositif de dérivation (30) qui est positionné fixé au-dessus d'un orifice d'évacuation (5b) dans un arbre principal (5) et qui régule la quantité d'huile évacuée par l'orifice d'évacuation. Ce dispositif de dérivation comprend : un boîtier (31) ayant, formée dans celui-ci une section creuse (36) dans laquelle l'huile s'écoule depuis l'orifice d'évacuation, le boîtier (31) ayant également un orifice de dérivation (37) à partir duquel l'huile s'étant écoulé dans la section creuse est évacuée ; un élément coulissant (40) se déplaçant au-dessus de l'orifice de dérivation et réglant le degré d'ouverture de l'orifice de dérivation ; et un élément de pression (41) pour presser l'élément coulissant vers un côté du boîtier à partir de l'autre côté de ce dernier. Lorsqu'il est déplacé radialement par la force centrifuge pendant la rotation de l'arbre principal, l'élément coulissant divise la section creuse en un premier espace (36A) sur le côté arbre principal et un second espace (36B) sur le côté élément de pression, et un passage d'équilibrage de pression (38) reliant le premier espace et le second espace, est formé dans la section creuse du boîtier.
PCT/JP2015/057315 2014-05-26 2015-03-12 Compresseur Ceased WO2015182214A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2016523187A JP6180630B2 (ja) 2014-05-26 2015-03-12 圧縮機

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014107894 2014-05-26
JP2014-107894 2014-05-26

Publications (1)

Publication Number Publication Date
WO2015182214A1 true WO2015182214A1 (fr) 2015-12-03

Family

ID=54698556

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2015/057315 Ceased WO2015182214A1 (fr) 2014-05-26 2015-03-12 Compresseur

Country Status (2)

Country Link
JP (1) JP6180630B2 (fr)
WO (1) WO2015182214A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020083309A1 (fr) * 2018-10-24 2020-04-30 艾默生环境优化技术(苏州)有限公司 Mécanisme d'alimentation en huile d'une machine rotative et machine rotative équipée d'un mécanisme d'alimentation en huile
WO2020083310A1 (fr) * 2018-10-24 2020-04-30 艾默生环境优化技术(苏州)有限公司 Mécanisme d'alimentation en huile de machine rotative et machine rotative
CN111089057A (zh) * 2018-10-24 2020-05-01 艾默生环境优化技术(苏州)有限公司 旋转机械的供油机构以及旋转机械
CN111089056A (zh) * 2018-10-24 2020-05-01 艾默生环境优化技术(苏州)有限公司 旋转机械的供油机构和具有该供油机构的旋转机械
CN120367817A (zh) * 2025-06-24 2025-07-25 珠海凌达压缩机有限公司 自适应供油组件、涡旋压缩机及空调器

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH056188U (ja) * 1991-04-15 1993-01-29 三菱電機株式会社 回転型圧縮機
JPH0733829B2 (ja) * 1986-02-03 1995-04-12 松下電器産業株式会社 スクロ−ル圧縮機
JPH0799151B2 (ja) * 1988-06-22 1995-10-25 三菱電機株式会社 スクロール圧縮機
JP2003254263A (ja) * 2002-03-04 2003-09-10 Daikin Ind Ltd スクロール圧縮機
US20090041603A1 (en) * 2007-08-02 2009-02-12 Danfoss Commercial Compressors Refrigerating compressor with variable-speed coils

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0733829B2 (ja) * 1986-02-03 1995-04-12 松下電器産業株式会社 スクロ−ル圧縮機
JPH0799151B2 (ja) * 1988-06-22 1995-10-25 三菱電機株式会社 スクロール圧縮機
JPH056188U (ja) * 1991-04-15 1993-01-29 三菱電機株式会社 回転型圧縮機
JP2003254263A (ja) * 2002-03-04 2003-09-10 Daikin Ind Ltd スクロール圧縮機
US20090041603A1 (en) * 2007-08-02 2009-02-12 Danfoss Commercial Compressors Refrigerating compressor with variable-speed coils

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020083309A1 (fr) * 2018-10-24 2020-04-30 艾默生环境优化技术(苏州)有限公司 Mécanisme d'alimentation en huile d'une machine rotative et machine rotative équipée d'un mécanisme d'alimentation en huile
WO2020083310A1 (fr) * 2018-10-24 2020-04-30 艾默生环境优化技术(苏州)有限公司 Mécanisme d'alimentation en huile de machine rotative et machine rotative
CN111089057A (zh) * 2018-10-24 2020-05-01 艾默生环境优化技术(苏州)有限公司 旋转机械的供油机构以及旋转机械
CN111089056A (zh) * 2018-10-24 2020-05-01 艾默生环境优化技术(苏州)有限公司 旋转机械的供油机构和具有该供油机构的旋转机械
EP3872348A4 (fr) * 2018-10-24 2022-08-10 Emerson Climate Technologies (Suzhou) Co., Ltd. Mécanisme d'alimentation en huile d'une machine rotative et machine rotative équipée d'un mécanisme d'alimentation en huile
US11885335B2 (en) 2018-10-24 2024-01-30 Copeland Climate Technologies (Suzhou) Co. Ltd. Oil supply mechanism of rotating machinery and rotating machinery having oil supply mechanism
CN120367817A (zh) * 2025-06-24 2025-07-25 珠海凌达压缩机有限公司 自适应供油组件、涡旋压缩机及空调器
CN120367817B (zh) * 2025-06-24 2025-09-12 珠海凌达压缩机有限公司 自适应供油组件、涡旋压缩机及空调器

Also Published As

Publication number Publication date
JPWO2015182214A1 (ja) 2017-04-20
JP6180630B2 (ja) 2017-08-16

Similar Documents

Publication Publication Date Title
US20180252216A1 (en) Scroll compressor
JP6180630B2 (ja) 圧縮機
JP5006444B2 (ja) 圧縮機及びそのオイル供給構造
JP6300829B2 (ja) 回転式圧縮機
WO2015162869A1 (fr) Compresseur a spirales
CN111133197B (zh) 涡旋式压缩机
JP6555543B2 (ja) スクロール圧縮機
JP5455763B2 (ja) スクロール圧縮機，冷凍サイクル装置
JPS63109291A (ja) スクロ−ル圧縮機
JP2007138868A (ja) スクロール圧縮機
JP6972391B2 (ja) スクロール圧縮機
CN107208633B (zh) 涡旋压缩机
WO2017158809A1 (fr) Compresseur
JP7051005B2 (ja) 圧縮機
JP2008031920A (ja) 回転式圧縮機
JP2017015054A (ja) シングルスクリュー圧縮機
JP2020045778A (ja) 圧縮機
JP4726914B2 (ja) スクロール流体機械
JP7262010B2 (ja) スクロール圧縮機
CN116498547A (zh) 涡旋型电动压缩机
KR102191566B1 (ko) 유분리 효율이 향상된 스크롤 압축기
JP2000027776A (ja) スクロ―ル型流体機械
JP2005344537A (ja) スクロール圧縮機
CN106414900A (zh) 涡旋式压缩机
JP2019148188A (ja) 圧縮機

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 15798921

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2016523187

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 15798921

Country of ref document: EP

Kind code of ref document: A1