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WO2009090888A1 - Machine rotative à fluide - Google Patents

Machine rotative à fluide Download PDF

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Publication number
WO2009090888A1
WO2009090888A1 PCT/JP2009/000157 JP2009000157W WO2009090888A1 WO 2009090888 A1 WO2009090888 A1 WO 2009090888A1 JP 2009000157 W JP2009000157 W JP 2009000157W WO 2009090888 A1 WO2009090888 A1 WO 2009090888A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
annular
piston
drive shaft
blade
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/JP2009/000157
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English (en)
Japanese (ja)
Inventor
Takashi Shimizu
Yoshitaka Shibamoto
Takazou Sotojima
Masanori Masuda
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.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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 Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of WO2009090888A1 publication Critical patent/WO2009090888A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • 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
    • F04C18/04—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 of internal-axis type
    • F04C18/045—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 of internal-axis type having a C-shaped piston
    • 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
    • F04C23/001—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 of similar working principle
    • 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
    • F04C2240/00—Components
    • 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

Definitions

  • the present invention relates to a rotary fluid machine, and more particularly to a rotary fluid machine in which a rotary mechanism having a cylinder having an annular cylinder chamber and an annular piston housed eccentrically in the cylinder chamber is arranged in two stages. Is.
  • a rotary fluid machine including an eccentric rotary piston mechanism having a cylinder having a cylinder chamber and a piston housed eccentrically in the cylinder chamber.
  • the eccentric rotary piston mechanism is configured such that the volume of the cylinder chamber fluctuates periodically by rotating the piston eccentrically with respect to the cylinder chamber.
  • the eccentric rotary piston mechanism is configured to suck fluid gas into the cylinder chamber and compress the sucked fluid gas to the outside of the cylinder chamber in accordance with the volume change of the cylinder chamber. ing.
  • Patent Document 1 discloses a rotary compressor as this type of rotary fluid machine.
  • the cylinder chamber constitutes a compression chamber
  • the compression chamber and the piston are each formed in an annular shape.
  • the annular piston is stored eccentrically in the cylinder chamber so as to divide the annular compression chamber into an outer compression chamber and an inner compression chamber, and a cylinder having an annular cylinder chamber with respect to the annular piston is provided. It is configured to rotate eccentrically.
  • the volume of the outer compression chamber and the inner compression chamber is increased with the rotation of the cylinder, whereby the refrigerant is sucked into each compression chamber, and then the volume of each compression chamber.
  • the refrigerant pressure gradually increases.
  • the discharge valve that closed each compression chamber is opened, and the refrigerant is discharged from the compression chamber.
  • the volume of each compression chamber periodically changes with the rotation of the annular cylinder, and the refrigerant pressure in each compression chamber also changes periodically with the periodic fluctuation of the volume of each compression chamber. If the change in the refrigerant pressure in the compression chamber is large, the output torque fluctuation of the drive shaft also increases, and in some cases, the vibration and noise of the rotary compressor increase.
  • Patent Document 2 discloses a rotary compressor in which the eccentric rotary piston mechanism of Patent Document 1 is arranged in two upper and lower stages.
  • the rotary compressor (60) of Patent Document 2 has an upper side with a disc-shaped middle plate (63) having a peripheral edge fixed to the inner wall of the casing (62). Housings (64, 65) are provided on the lower side and the lower side, respectively.
  • the cylinder (66) and the annular piston (67) are housed in the upper space surrounded by the upper housing (65) and the middle plate (63), and are surrounded by the lower housing (64) and the middle plate (63).
  • a cylinder (66) and an annular piston (67) are housed in the lower space.
  • the rotary compressor (60) has an inner side formed on the upper side and the lower side, respectively, in which the phase of the fluctuation cycle of the volume of the outer compression chamber (68) formed on the upper side and the lower side is shifted from each other by 180 degrees.
  • the phase of the fluctuation cycle of the volume of the compression chamber (69) is configured to be shifted from each other by 180 degrees.
  • the torque fluctuation of the drive shaft (70) generated with the change of the refrigerant pressure in the upper compression chambers (68, 69) is reduced in the lower compression chambers (68, 69).
  • This can be offset by torque fluctuations of the drive shaft (70) that occur with changes in the refrigerant pressure. Therefore, the torque fluctuation of the drive shaft (70) can be suppressed as a whole in the rotary compressor (60), and the vibration and noise of the rotary compressor (60) can be reduced.
  • the present invention has been made in view of such a point, and an object of the present invention is to overlap a rotation mechanism having a cylinder having an annular cylinder chamber and an annular piston housed eccentrically in the cylinder chamber in two stages.
  • the number of components is reduced as much as possible while reducing vibration and noise, and the cost of the rotary fluid machine is reduced.
  • an eccentric rotary piston mechanism (20) and a drive mechanism (30) having a drive shaft (33) for driving the eccentric rotary piston mechanism (20) are provided in the casing (10).
  • the eccentric rotating piston mechanism (20) includes a first rotating mechanism (20a) and a second rotating mechanism (20b), and the first rotating mechanism (20a) and the second rotating mechanism (20b) are annular.
  • the first cylinder (21) and the second cylinder (21) having cylinder chambers (C1, C2, C3, C4) and the annular cylinder chambers (C1, C2, C3, C4) are connected to the outer cylinder chambers (C1, C3).
  • each annular piston (22, 22) presupposes a rotary fluid machine that rotated eccentrically relative to the respective cylinder (21, 21).
  • the first cylinder (21) and the second cylinder (21) face each other in the axial direction and form an internal space (S1) between the cylinders (21, 21).
  • An annular cylinder chamber (C1, C2, C3, C4) is provided on both sides in the axial direction of (S1).
  • the first annular piston (22) and the second annular piston (22) face each other in the axial direction, and one side of each annular piston (22, 22) is attached to the surface of the end plate (22c, 22c).
  • the axial centers of the annular pistons (22, 22) are decentered in opposite directions around the axis of the drive shaft (33), and the back surfaces of the end plates (22c, 22c) are aligned with each other. Is attached to the drive shaft (33).
  • the annular pistons (22, 22) are fixed to the drive shaft (33) so that the rear surfaces of the end plates (22c, 22c) of the annular pistons (22, 22) are aligned with each other.
  • the eccentric rotary piston mechanism (20) can be configured without using the middle plate unlike the conventional case.
  • Each annular piston (22, 22) has a drive shaft (33) so that the rotation shaft of each annular piston (22, 22) is decentered in the opposite direction around the axis of the drive shaft (33). ).
  • the phases of the volume fluctuation periods in the two outer cylinder chambers (C1, C3) are shifted from each other by 180 degrees
  • the phases of the volume fluctuation periods in the two inner cylinder chambers (C2, C4) are shifted from each other by 180 degrees. Therefore, the torque fluctuation of the drive shaft (33) generated in the first rotation mechanism (20a) can be canceled out by the torque fluctuation of the drive shaft (33) generated in the second rotation mechanism (20b).
  • the torque fluctuation of the drive shaft (33) can be kept small.
  • the annular pistons (22, 22) are disposed on the surface side of the end plates (22c, 22c) of the first annular piston (22) and the second annular piston (22).
  • a first rotation prevention mechanism (23) and a second rotation prevention mechanism (23) for preventing the rotation of the rotation are respectively provided.
  • each rotation prevention mechanism (23, 23) is provided on the surface side of the end plate (22c, 22c) of each annular piston (22, 22), the rotation prevention mechanism is the end plate (22c). , 22c), the back surfaces of the end plates (22c, 22c) can be easily aligned with each other.
  • the first blade (23) constitutes a first rotation prevention mechanism (23), and the second blade (23) constitutes a second rotation prevention mechanism (23).
  • Each of the annular pistons (22, 22) has a straight portion (22d, 22d) continuous with another portion in a part of the circumferential direction. Further, each of the blades (23, 23) is formed integrally with the outer blade portion (23a) defining the outer cylinder chamber (C1, C3) and the outer blade portion (23a), and the inner cylinder chamber (C2 , C4) and an inner blade part (23b) that divides the linear piston (22d) of each annular piston (22, 22) between the outer blade part (23a) and the inner blade part (23b).
  • each cylinder (21, 21) has a blade groove (28) in which the outer blade portion (23a, 23a) and the inner blade portion (23b, 23b) are slidably fitted in the cylinder radial direction. Are formed respectively.
  • the blades (23, 23) slide in the radial direction with respect to the cylinders (21, 21) by sliding in the blade grooves (28, 28).
  • the movement in the direction orthogonal to the cylinder radial direction is restricted with respect to (21, 21).
  • the annular pistons (22, 22) are fitted into the recesses (23c) of the blades (23, 23) by the linear portions (22d) of the annular pistons (22, 22).
  • (23, 23) slides in the cylinder radial direction with respect to each cylinder (21, 21).
  • each annular piston (22, 22) slides in the recess (23c) of each blade (23, 23) by the linear portion (22d) of each annular piston (22, 22), thereby each cylinder ( Slides in a direction perpendicular to the cylinder radial direction with respect to 21 and 21). Thereby, each annular piston (22, 22) is eccentrically rotated.
  • each annular piston (22, 22) slides in a direction perpendicular to the cylinder radial direction with respect to each blade (23, 23), and only moves in the cylinder radial direction together with each blade (23, 23). And the displacement in the rotational direction of each annular piston (22, 22) is restricted. Thereby, rotation of each annular piston (22, 22) is regulated by each blade (23, 23).
  • the cylinder chambers (C3, C4) provided in the cylinders (21, 21) and the casing (10) on the high pressure side Discharge ports (45, 46) that communicate with each other, and a through passage that penetrates the lubricating oil stored in the lower part of the casing (10) from the lower end surface of the drive shaft (33) to the outer peripheral surface of the drive shaft (33)
  • Oil supply means (34) for supplying a sliding surface formed between the end plates (22c, 22c) of the two annular pistons (22, 22) via (38).
  • An annular seal member (24) is provided so as to be sandwiched between the end plates (22c, 22c) of the two annular pistons (22, 22).
  • the high-pressure gas in each cylinder chamber (C3, C4) on the high-pressure side is discharged from the discharge port (45, 46) into the casing (10).
  • the inside of the casing (10) is in a high pressure state.
  • the lubricating oil stored in the casing (10) is also in a high pressure state.
  • the high-pressure lubricating oil is supplied to the sliding surface through the oil supply means (34).
  • each annular piston (22, 22) is pressed against each cylinder (21, 21) by the pressure between the end plates (22c, 22c) of the both annular pistons (22, 22).
  • the pressure between the end plates (22c, 22c) is also high. Therefore, if the pressure between the end plates (22c, 22c) becomes too high, the annular piston (22, 22) may be excessively pressed against the cylinder (21, 21).
  • the annular seal member (24) partitions the end plates (22c, 22c) of both annular pistons (22, 22) into an inner side and an outer side of the annular seal member (24). can do.
  • the end plates (22c, 22c) By partitioning the end plates (22c, 22c), only the inner part of the annular seal member (24) can be brought into a high pressure state. That is, the high-pressure region can be made narrower than when no annular seal member (24) is provided. Thereby, it can suppress that an annular piston (22, 22) is pressed against a cylinder (21, 21) excessively.
  • the eccentric rotary piston mechanism (20) can be configured without using a middle plate. Further, the torque fluctuation of the drive shaft (33) generated in the first rotation mechanism (20a) can be canceled out by the torque fluctuation of the drive shaft (33) generated in the second rotation mechanism (20b), so that the rotary fluid As a whole machine, the torque fluctuation of the drive shaft (33) can be kept small. Therefore, it is possible to reduce the cost by reducing the middle plate while reducing the vibration and noise due to the torque fluctuation of the drive shaft (33).
  • each rotation prevention mechanism (23, 23) is provided on the surface side of the end plate (22c, 22c) of each annular piston (22, 22), the rotation prevention mechanism is provided. Compared with the case where it is provided on the back side of the end plate (22c, 22c), the back sides of the end plate (22c, 22c) can be easily aligned. Thereby, it becomes easy to delete the middle plate provided in the conventional rotary fluid machine, and cost reduction can be achieved.
  • each blade (23, 23) provided on the surface side of the end plate (22c, 22c) of each annular piston (22, 22) is provided with each annular piston (22, 22). It also serves as a rotation prevention mechanism of 22). Therefore, the back surfaces of the end plates (22c, 22c) can be matched with each other without providing a rotation prevention mechanism. Thereby, it becomes easy to delete the middle plate provided in the conventional rotary fluid machine, and cost reduction can be achieved.
  • the annular piston (22, 22) is connected to the cylinder (21, 21) while reducing the number of the annular seal members (24). It is possible to suppress excessive pressing on the surface. That is, in the conventional case, since the middle plate is provided between the two movable members, the middle plate and one movable member, and the middle plate and the other movable member, respectively. It is necessary to provide an annular seal member (24).
  • annular seal member (24) may be provided between the end plates (22c, 22c) of both annular pistons (22, 22). Thereby, cost reduction can be achieved. Moreover, it can suppress that an annular piston (22,22) is pressed excessively by setting so that the inner side of an annular seal member (24) may become small.
  • Rotary compressor (Rotary fluid machine) 10 Casing 20 Compression mechanism (Eccentric rotation type piston mechanism) 21 cylinder 21a outer cylinder part 21b inner cylinder part 21c cylinder side end plate 22 annular piston 22a piston part 22b bearing part 22c piston side end plate 23 blade 23a outer blade part 23b inner blade part 23c recess 24 seal ring (seal member) 30 Electric motor (drive mechanism) 33 Drive shaft 34 Oil pump (oil supply means) 35 Back pressure adjustment mechanism 36 Communication passage 37 Check valve 38 Oil supply passage (through passage) 41 Suction port 44 Through hole 45 Outer discharge port 46 Inner discharge port
  • an electric motor (drive mechanism) (30) and a compression mechanism (eccentric rotary piston mechanism) (20) are housed in a casing (10). It is a rotary compressor (1) configured in a completely sealed type.
  • the rotary compressor (1) is provided, for example, in a refrigerant circuit of an air conditioner, and is used to compress gas refrigerant sucked from an evaporator and discharge it to a condenser.
  • the casing (10) includes a barrel (11) formed in a vertically long cylindrical shape, an upper end plate (12) fixed to the upper end of the barrel (11), and a lower end of the barrel (11). And a lower end plate (13) fixed to the airtight container.
  • the upper end plate (12) is provided with a discharge pipe (15) passing through the upper end plate (12).
  • the discharge pipe (15) communicates with the inside of the casing (10), and the inlet thereof opens into a space above the electric motor (30) disposed in the upper part of the casing (10).
  • the body (11) is provided with two suction pipes (14) passing through the body (11). These suction pipes (14) are respectively connected to a compression mechanism (20) disposed in the lower part of the casing (10).
  • the rotary compressor (1) is configured such that the refrigerant compressed by the compression mechanism (20) is discharged into the casing (10) (S2) and then passed through the discharge pipe (15) to the casing (10). It is configured to be sent out. Therefore, during the operation of the rotary compressor (1), the inside of the casing (10) becomes a high-pressure space (S2).
  • the electric motor (30) includes a stator (31) and a rotor (32).
  • the stator (31) has a cylindrical shape and is fixed to the inner surface of the body (11) of the casing (10).
  • a drive shaft (33) is connected to the rotor (32), and the drive shaft (33) is configured to rotate together with the rotor (32).
  • An oil pump (oil supply means) (34) is provided at the lower end of the drive shaft (33). And by this oil pump (34), the lubricating oil in the reservoir (59) provided at the bottom of the casing (10) is passed through the oil supply passage (38) to each sliding part of the compression mechanism (20), And it supplies to the sliding surface formed between the annular pistons (22) arrange
  • the upper and lower eccentric portions (33b, 63b) in FIG. 1 are provided adjacent to each other. These eccentric portions (33b, 63b) are formed to have a larger diameter than the upper and lower portions of the eccentric portions (33b, 63b).
  • the axes of the eccentric portions (33b) are eccentric in opposite directions around the axis of the drive shaft (33).
  • the compression mechanism (20) includes two compression units (20a, 20b) that constitute the first rotation mechanism and the second rotation mechanism. These compression parts (20a, 20b) have substantially the same configuration except that the axis of the eccentric part (33b) described above is eccentric, and these compression parts (20a, 20b) are adjacent in the vertical direction. Has been placed.
  • the upper and lower compression parts (20a, 20b) include a cylinder (21) having an annular cylinder chamber (C1, C2, C3, C4) and the annular cylinder chamber (C1, C2, C3, C4).
  • An annular piston (22) housed eccentrically in the annular cylinder chamber (C1, C2, C3, C4) so as to partition into an outer cylinder chamber (C1, C3) and an inner cylinder chamber (C2, C4);
  • Each has a blade (23) that partitions the outer cylinder chamber (C1, C3) and the inner cylinder chamber (C2, C4) into a high-pressure side and a low-pressure side, respectively.
  • the annular piston (22) is configured to perform eccentric rotational movement with respect to the cylinder (21) in the cylinder chamber (C1, C2, C3, C4).
  • the upper and lower cylinders (21, 21) are each provided with an outer cylinder part (21a), an inner cylinder part (21b), and a cylinder side end plate (21c).
  • Each cylinder (21) is formed by connecting the end portion of the outer cylinder portion (21a) and the end portion of the inner cylinder portion (21b) with a cylinder side end plate (21c).
  • the drive shaft (33) passes through the central portion of both cylinders (21, 21), and the drive shaft (33) is formed on the inner peripheral surface of the through hole through which the drive shaft (33) passes.
  • the upper and lower cylinders (21, 21) are end faces of the outer cylinder portions (21a) of the cylinders (21, 21) so that an internal space (S1) is formed between the cylinders (21, 21). They are fixed in close contact with each other.
  • the outer peripheral surfaces of both cylinders (21, 21) fixed in this way are fixed to the inner peripheral surface of the casing (10) by welding or the like.
  • Two annular pistons (22, 22) are accommodated in the internal space (S1).
  • Each annular piston (22, 22) includes an annular piston portion (22a), a bearing portion (22b), and a piston side end plate (22c).
  • Each annular piston (22) is formed by connecting the end portion of the piston portion (22a) and the end portion of the bearing portion (22b) with a piston side end plate (22c).
  • the upper and lower annular pistons (22) are fixed to the drive shaft (33) so that the bearing portions (22b) are fitted to the eccentric portions (33b, 63b) of the drive shaft (33). ing.
  • the upper and lower eccentric parts (33b, 63b) are eccentric in the opposite directions with the axis of both eccentric parts (33b, 63b) centering on the axis of the drive shaft (33). It is formed to do. Therefore, the upper and lower annular pistons (22, 22) fitted to the eccentric parts (33b, 63b) are also centered on the axis of the drive shaft (33). Are eccentric in opposite directions.
  • a minute gap is formed between the upper and lower piston side end plates (22c), and a seal ring (24) is provided in this minute gap.
  • the seal ring (24) divides the minute gap into an inner side and an outer side, and the inner side of the seal ring (24) is pressurized via an oil supply passage (38) of the drive shaft (33). It communicates with the space (S2).
  • the minute gap is in a high pressure state.
  • the pressure inside the seal ring (24) presses the upper annular piston (22) toward the upper cylinder (21), and the lower annular piston (22) toward the lower cylinder (21). Configures the back pressure for pressing.
  • the outside of the seal ring (24) communicates with an internal space (S1) formed between both cylinders (21, 21).
  • the pressure in the internal space (S1) is caused by the lubricant that enters beyond the seal ring (24) and the lubricant that leaks from the bearing through the cylinder chamber (C1, C2, C3, C4). Although it rises, it is comprised so that it may not become more than predetermined pressure by the back pressure adjustment mechanism (35) mentioned later.
  • the upper and lower blades (23) each have an outer blade portion (23a) that partitions the outer cylinder chamber (C1, C3) and an inner blade portion (23b) that partitions the inner cylinder chamber (C2, C4).
  • each compression section (20a, 20b) the cylinder (21) and the annular piston (22) are arranged as shown in FIG.
  • the annular piston (22) is formed continuously without being divided by the piston part (22a), and a part of the piston part (22a) in the circumferential direction is orthogonal to the radial direction passing through the center line of the blade.
  • a straight portion (22d) is formed.
  • the part corresponding to the linear part (22d) of the piston part (22a) is orthogonal to the radial direction.
  • a straight line portion is formed.
  • a blade groove (28) for slidably fitting the blade (23) fitted to the piston part (22a) is formed in the straight part of both cylinder parts (21a, 21b). It is continuously formed in a straight line along the direction.
  • the blades (23) are slidably fitted into the blade grooves (28) while the recesses (23c) are slidably fitted to the linear portions (22d) of the piston portion (22a).
  • the outer blade portion (23a) partitions the outer cylinder chamber (C1, C3) into the high pressure side (C1) and the low pressure side (C3)
  • the inner blade portion (23b) is the inner cylinder chamber.
  • (C2, C4) is divided into a high pressure side (C2) and a low pressure side (C4).
  • the outer peripheral surface of the inner cylinder part (21b) and the inner peripheral surface of the outer cylinder part (21a) are formed by cylindrical surfaces arranged concentrically with each other.
  • An annular cylinder chamber (C1, C2, C3, C4) as a compression chamber is formed between the inner peripheral surface of the outer cylinder portion (21a) and the outer peripheral surface of the inner cylinder portion (21b).
  • the piston portion (22a) of the annular piston (22) is positioned in this cylinder chamber (C1, C2, C3, C4). That is, the outer peripheral surface of the piston part (22a) is formed with a smaller diameter than the inner peripheral surface of the outer cylinder part (21a), and the inner peripheral surface of the piston part (22a) is smaller than the outer peripheral surface of the inner cylinder part (21b). Is also formed in a large diameter.
  • an outer cylinder chamber (C1, C3) is formed between the outer peripheral surface of the piston portion (22a) and the inner peripheral surface of the outer cylinder portion (21a), while the inner peripheral surface of the piston portion (22a)
  • Inner cylinder chambers (C2, C4) are formed between the inner cylinder part (21b) and the outer peripheral surface.
  • Each annular piston (22) and each cylinder (21) are in a state where the outer peripheral surface of the piston portion (22a) and the inner peripheral surface of the outer cylinder portion (21a) are substantially in contact at one point (strictly speaking, In the state where there is a minute gap of micron order, but refrigerant leakage through the minute gap does not matter), the inner peripheral surface of the piston part (22a) and the inner cylinder at a position that is 180 degrees out of phase with the contact point.
  • the outer peripheral surface of the portion (21b) is substantially in contact with one point.
  • Each cylinder (21) is formed with a suction port (41) that penetrates the outer cylinder portion (21a) in the cylinder radial direction.
  • the suction port (41) has one end opened to the low pressure chamber (C1) of the outer cylinder chamber (C1, C3), and the other end is inserted with a suction pipe (14).
  • the piston part (22a) has a through hole (44) communicating the low pressure chamber (C1) of the outer cylinder chamber (C1, C3) and the low pressure chamber (C2) of the inner cylinder chamber (C2, C4). Is formed.
  • each cylinder (21) is formed with an outer discharge port (45) and an inner discharge port (46) that penetrate the cylinder side end plate (21c) in the thickness direction.
  • the opening end on the annular piston (22) side of the outer discharge port (45) faces the high pressure chamber (C3) of the outer cylinder chamber (C1, C3), and the opening on the annular piston (22) side of the inner discharge port (46) The end faces the high pressure chamber (C4) of the inner cylinder chamber (C2, C4).
  • the outer discharge port (45) and the inner discharge port (46) are each provided with a discharge valve (not shown) including a check valve for opening and closing the port.
  • the lower cylinder (21) has a communication passage (36) and a check valve (37) provided in the communication passage (36) for opening and closing the communication passage (36).
  • a back pressure adjusting mechanism (35) is provided.
  • the communication path (36) is configured to communicate the internal space (S1) and the suction port (41).
  • the check valve (37) has a valve chamber in which a fluid inlet and a fluid outlet are formed, and a ball valve and a coil spring are accommodated in the valve chamber.
  • a valve seat is provided at the fluid inflow port, and a coil spring is attached to urge the ball valve toward the valve seat.
  • the upper end surface of the upper inner cylinder part (21b) (the lower end surface in FIG. 1) is in sliding contact with the upper end surface of the upper piston side end plate (22c).
  • the tip end surface (upper end surface in FIG. 1) of the lower inner cylinder portion (21b) is in sliding contact with the lower end surface of the end plate (22c).
  • the tip surface (upper end surface in FIG. 1) of the upper piston portion (22a) is on the upper surface of the cylinder chamber (C1, C2, C3, C4) except for the portion where the blade (23) is fitted.
  • the tip surface (lower end surface in FIG. 1) of the lower piston portion (22a) is in sliding contact with the cylinder chamber (C1, C2, C3, C4) except for the portion where the blade (23) is fitted. It is in sliding contact with the lower surface.
  • the upper surface of the upper blade (23) is in sliding contact with the lower end surface of the upper cylinder end plate (21c), and the lower surface of the lower blade (23) is the upper end surface of the lower cylinder end plate (21c). Is in sliding contact.
  • the tip surface (upper end surface in FIG. 1) of the upper bearing portion (22b) is in sliding contact with the flat plate portion inside the upper inner cylinder portion (21b), and the tip surface of the lower bearing portion (22b).
  • the lower end surface of FIG. 1 is in sliding contact with the flat plate portion inside the lower inner cylinder portion (21b).
  • the cylinder pistons (C1, C2, C3, C4) in an airtight state are formed by the sliding contact between the annular piston (22), the cylinders (21, 21), and the blades (23). ing.
  • the annular piston (22) slides in the direction perpendicular to the cylinder radial direction with respect to the blade (23) and only moves in the cylinder radial direction together with the blade (23).
  • the displacement in the rotational direction is restricted. That is, the blade (23) constitutes a rotation prevention mechanism that restricts the rotation of the annular piston (22, 22).
  • the piston part (22a) is moved relative to the outer cylinder part (21a) and inner cylinder part (21b) of each cylinder (21) Revolving, the compression unit (20a) performs a predetermined compression operation.
  • the volume of the low-pressure chamber (C1) is almost the minimum in the state shown in FIG. 3B, from which the drive shaft (33) rotates clockwise in the figure.
  • the volume of the low pressure chamber (C1) increases, and the refrigerant passes through the suction pipe (14) and the suction port (41). Inhaled into chamber (C1).
  • the drive shaft (33) makes one revolution and returns to the state of FIG. 3 (B)
  • the suction of the refrigerant into the low pressure chamber (C1) is completed.
  • this low pressure chamber (C1) becomes a high pressure chamber (C3) where the refrigerant is compressed, and a new low pressure chamber (C1) is formed across the blade (23).
  • the suction of the refrigerant is repeated in the low pressure chamber (C1), while the volume of the high pressure chamber (C3) decreases, and the refrigerant is compressed in the high pressure chamber (C3).
  • the discharge valve is opened by the high pressure refrigerant in the high pressure chamber (C3), and the high pressure refrigerant is discharged from the discharge space to the casing (10 ) Flows out into the high-pressure space (S2).
  • the volume of the low-pressure chamber (C2) is almost the minimum in the state of FIG. 3 (F), and the drive shaft (33) rotates clockwise from here.
  • the volume of the low pressure chamber (C2) increases as the state changes from 3 (G) to FIG. 3 (E), and the refrigerant flows into the suction pipe (14), the suction port (41), and the through hole (44). And is sucked into the low pressure chamber (C2) of the inner cylinder chamber (C2, C4).
  • the discharge valve is opened by the high pressure refrigerant in the high pressure chamber (C4), and the high pressure refrigerant is discharged from the discharge space to the casing (10 ) Flows out into the high-pressure space (S2).
  • the sliding part of the compression mechanism (20) is lubricated by the lubricating oil in the storage part (59).
  • the lubricating oil in the storage section (59) is compressed by being pushed upward in the oil supply passage (38) of the drive shaft (33) by the oil pump (34) at the lower end of the drive shaft (33).
  • the bearings (16) of the mechanism (20) and the minute gaps between the upper and lower annular pistons (22) are supplied to the inner part of the seal ring (24). Then, the lubricating oil supplied to the inner part flows over the seal ring (24) and flows into the internal space (S1) to increase the pressure in the internal space (S1).
  • the fluid inlet of the back pressure adjustment mechanism (35) opens, and the internal space (S1) communicates with the suction port (41), and the pressure in the internal space (S1) decreases.
  • the pressure in the internal space (S1) becomes smaller than the elastic force of the coil spring of the back pressure adjusting mechanism (35)
  • the fluid inlet of the back pressure adjusting mechanism (35) is closed, and the internal space (S1 ) And the suction port (41) are blocked, and the pressure in the internal space (S1) does not decrease.
  • the annular piston (22, 22) is prevented from being excessively pressed against the cylinder (21, 21). ing.
  • the lubricating oil that has flowed into the internal space (S1) over the seal ring (24) is discharged to the suction port (41) through the back pressure adjustment mechanism (35).
  • the lubricating oil discharged to the suction port (41) is sucked into the compression mechanism (20) together with the refrigerant, compressed in each cylinder chamber (C1, C2, C3, C4), and then into the casing (10).
  • the high pressure space (S2) is discharged to return to the reservoir (59).
  • the lubricating oil that has flowed into the internal space (S1) is agitated on the outer peripheral surface of the annular piston (22, 22) by the eccentric rotational movement of each annular piston (22, 22). At this time, even if the annular piston (22, 22) rotates eccentrically, the volume of the internal space (S1) outside the outer peripheral surface of the annular piston (22, 22) is constant. Therefore, the stirring loss of the lubricating oil by the annular pistons (22, 22) does not change.
  • the compression mechanism (20) in which the compression parts (20a, 20b) are arranged in two upper and lower stages without using a middle plate.
  • the compression mechanism (20) is configured such that the rotation shafts of the annular pistons (22, 22) are eccentric in opposite directions around the axis of the drive shaft (33).
  • the phases of the volume fluctuation periods in the outer compression chambers (C1, C3) formed in the upper and lower compression sections (20a, 20b) are shifted from each other by 180 degrees, and formed on the upper and lower sides, respectively.
  • the phases of the volume fluctuation periods in the inner compression chambers (C2, C4) are shifted from each other by 180 degrees. From this, the torque fluctuation of the drive shaft (33) generated in the upper compression section (20a) can be offset by the torque fluctuation of the drive shaft (33) generated in the lower compression section (20b), As a whole rotary compressor, the torque fluctuation of the drive shaft (33) can be kept small.
  • the present embodiment it is possible to prevent the rotation of the annular pistons (22, 22) without the middle plate. That is, in the conventional case, since the middle plate is provided between the upper and lower movable members (the cylinder (66) in FIG. 4 and the annular piston in this embodiment), the middle plate is provided between the movable member and the middle plate. It is easy to attach an Oldham joint or the like for preventing the movable member from rotating. However, in the case of this embodiment, since there is no middle plate, it is not easy to attach an Oldham joint or the like. Therefore, according to the present embodiment, the rotation of the annular pistons (22, 22) can be prevented by providing the blades (23, 23) with a rotation prevention function.
  • the rotation prevention mechanism on the surface side of the piston side end plate (22c, 22c), the back surfaces of the piston side end plate (22c, 22c) can be easily aligned. Thereby, it becomes easy to delete the middle plate provided in the conventional rotary compressor, and the cost of the rotary compressor (1) can be reduced.
  • the seal ring (24) can divide a minute gap between both the annular pistons (22, 22) into the inside and the outside of the seal ring (24). Then, by partitioning this minute gap, only the inner part of the seal ring (24) can be brought into a high pressure state. That is, when the diameter of the seal ring (24) is set large, the range of the high pressure state of the minute gap is widened, and the back pressure is increased. On the other hand, when the diameter of the seal ring (24) is set to be small, the back pressure is reduced. Thus, by setting the diameter of the seal ring (24) according to the rotary compressor (1), the annular piston (22, 22) is prevented from being excessively pressed against the cylinder (21, 21). be able to.
  • the annular seal member is provided between the upper surface of the middle plate and the upper movable member, and between the lower surface of the middle plate and the lower movable member. (24) needs to be provided, but in this embodiment, only one seal ring (24) needs to be provided in the minute gap between both annular pistons (22, 22), thereby reducing costs. Can do.
  • the annular cylinder chamber (C1, C2, C3, C4) of the cylinder (21) constitutes a compression chamber.
  • the present invention is not limited to this, and the annular cylinder chamber (C1, C2, C3, C4) may constitute an expansion chamber.
  • a swing bush that supports the annular pistons (22, 22) in a swingable manner may be provided.
  • the present invention is useful for a rotary fluid machine in which a rotating mechanism having a cylinder having an annular cylinder chamber and an annular piston housed eccentrically in the cylinder chamber is arranged in two stages. .

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

Abstract

La présente invention concerne une machine rotative à fluide (1) présentant un premier piston annulaire (22) et un second piston annulaire (22) se faisant face dans le sens axial. Un côté de chaque piston annulaire (22, 22) est monté sur une surface d'une plaque d'extrémité correspondante (22c, 22c). Les axes des pistons annulaires (22, 22) sont excentriques l'un par rapport à l'autre dans des directions opposées par rapport à l'axe d'un arbre d'entraînement (33) et sont montés sur l'arbre d'entraînement (33) de telle sorte que les plaques d'extrémité (22c, 22c) soient reliées dos à dos l'une à l'autre.
PCT/JP2009/000157 2008-01-18 2009-01-16 Machine rotative à fluide Ceased WO2009090888A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008-009378 2008-01-18
JP2008009378A JP4609496B2 (ja) 2008-01-18 2008-01-18 回転式流体機械

Publications (1)

Publication Number Publication Date
WO2009090888A1 true WO2009090888A1 (fr) 2009-07-23

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PCT/JP2009/000157 Ceased WO2009090888A1 (fr) 2008-01-18 2009-01-16 Machine rotative à fluide

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JP (1) JP4609496B2 (fr)
WO (1) WO2009090888A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102444582A (zh) * 2010-09-30 2012-05-09 广东美芝制冷设备有限公司 旋转式压缩机
JP2016065532A (ja) * 2014-09-26 2016-04-28 株式会社イワキ 容積型ポンプ
WO2017063588A1 (fr) * 2015-10-15 2017-04-20 珠海格力节能环保制冷技术研究中心有限公司 Compresseur à capacité variable à double étage et système de climatisation doté de celui-ci

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022152228A1 (fr) * 2021-01-18 2022-07-21 艾默生环境优化技术(苏州)有限公司 Compresseur à spirale

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Publication number Priority date Publication date Assignee Title
JPS5122202B1 (fr) * 1970-03-17 1976-07-08
JPS61151090U (fr) * 1985-03-13 1986-09-18
JPS62102801U (fr) * 1985-12-19 1987-06-30
JPS6360091U (fr) * 1986-10-06 1988-04-21
JPH0650274A (ja) * 1992-07-02 1994-02-22 Matsushita Electric Ind Co Ltd スクロール圧縮機
JP2005320929A (ja) * 2004-05-11 2005-11-17 Daikin Ind Ltd 回転式流体機械

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4104047B2 (ja) * 2001-05-18 2008-06-18 松下電器産業株式会社 スクロール圧縮機
JP4779889B2 (ja) * 2005-05-23 2011-09-28 ダイキン工業株式会社 回転式圧縮機

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5122202B1 (fr) * 1970-03-17 1976-07-08
JPS61151090U (fr) * 1985-03-13 1986-09-18
JPS62102801U (fr) * 1985-12-19 1987-06-30
JPS6360091U (fr) * 1986-10-06 1988-04-21
JPH0650274A (ja) * 1992-07-02 1994-02-22 Matsushita Electric Ind Co Ltd スクロール圧縮機
JP2005320929A (ja) * 2004-05-11 2005-11-17 Daikin Ind Ltd 回転式流体機械

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102444582A (zh) * 2010-09-30 2012-05-09 广东美芝制冷设备有限公司 旋转式压缩机
JP2016065532A (ja) * 2014-09-26 2016-04-28 株式会社イワキ 容積型ポンプ
WO2017063588A1 (fr) * 2015-10-15 2017-04-20 珠海格力节能环保制冷技术研究中心有限公司 Compresseur à capacité variable à double étage et système de climatisation doté de celui-ci

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JP2009167976A (ja) 2009-07-30

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