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WO2010070757A1 - Machine hydraulique à spirale - Google Patents

Machine hydraulique à spirale Download PDF

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Publication number
WO2010070757A1
WO2010070757A1 PCT/JP2008/073096 JP2008073096W WO2010070757A1 WO 2010070757 A1 WO2010070757 A1 WO 2010070757A1 JP 2008073096 W JP2008073096 W JP 2008073096W WO 2010070757 A1 WO2010070757 A1 WO 2010070757A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotation
scroll
shaft
fluid machine
turning
Prior art date
Application number
PCT/JP2008/073096
Other languages
English (en)
Japanese (ja)
Inventor
富石 黄
光宣 黄
Original Assignee
リッチストーンリミテッド
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 リッチストーンリミテッド filed Critical リッチストーンリミテッド
Priority to CN200880132361.4A priority Critical patent/CN102257276B/zh
Priority to KR1020117015605A priority patent/KR101300597B1/ko
Priority to PCT/JP2008/073096 priority patent/WO2010070757A1/fr
Priority to JP2010542792A priority patent/JP5433831B2/ja
Publication of WO2010070757A1 publication Critical patent/WO2010070757A1/fr
Priority to US13/134,873 priority patent/US20110300013A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F04C18/0223—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 with symmetrical double wraps
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F04C29/06—Silencing
    • 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 an eccentric orbiting drive type scroll fluid machine suitable for high-speed operation.
  • the scroll fluid machine has a fixed scroll in which a spiral wrap is erected on an end plate, and an operating part configured by combining similar orbiting scrolls.
  • the orbiting scroll is fixed to the shaft of the driving device and is rotated without rotating, the working fluid flowing from the suction pipe is compressed and discharged from the discharge pipe, thereby functioning as a compressor or a blower.
  • the high-pressure working fluid flowing from the inlet of the fixed scroll is expanded and discharged from the outlet, it functions as an expander that extracts power from the shaft of the drive device.
  • An eccentric swivel drive device having a swivel axis has been proposed as a drive device used in a scroll fluid machine.
  • a scroll fluid machine disclosed in Japanese Patent No. 3761503 has an eccentric turning drive device and a fluid machine body driven by the eccentric turning drive device.
  • the turning shaft of the eccentric turning drive device is attached to penetrate the turning scroll of the fluid machine main body.
  • first and second eccentric orbiting support means for supporting the orbiting shaft so as to be eccentrically rotatable with respect to the fixed scroll of the fluid machine body.
  • orbiting bearings that support the orbiting shaft are provided on both sides of the orbiting scroll.
  • a rotary bearing is provided on the outer side of both rotary bearings via a rotating body whose axis coincides with the rotary shaft of the eccentric rotary drive device. For this reason, the rotary bearing is driven by the slewing shaft during operation, but since a mechanism for synchronously rotating both slewing bearings is not provided, the rotational resistance of the rotary bearing and the slewing bearing is applied in the movement direction of the slewing shaft. As a result, the smooth drive of the swivel shaft is hindered, and there is a risk that the laps will come into contact with each other to generate noise, and the lap may be worn or seized. It is an object of the present invention to provide a structure that prevents the wraps from contacting each other and prevents noise, wrap wear and seizure, so that the swivel shaft can be smoothly driven and prevented from swinging.
  • the present invention has been made to solve the above problems.
  • the present invention provides a highly reliable scroll fluid machine that has a structure with less resistance in the direction of motion and that does not generate vibration noise due to contact between the laps, and that the laps are not worn or seized.
  • Main features For this reason, even if the rotational speed increases and the centrifugal force of the orbiting scroll increases, or the differential pressure between the discharge pressure and the suction pressure increases and the radial load acting on the orbiting shaft increases, Means are provided to prevent displacement in the direction.
  • the swivel shaft eccentrically supported by the rotation shaft and rotatably supported, the rotation prevention means for preventing the rotation of the swivel shaft, and the swivel drive portion of the swivel shaft are fitted into a spiral wrap on both sides.
  • the orbiting shaft passes through the actuating portion and guides the fixed scroll located at the outermost portion.
  • one end of the swivel shaft is guided by the guide mechanism and swivels to generate a load that cancels a radial load acting on the swivel shaft.
  • the guide mechanism is a rotation prevention guide or a balance bearing attached to the outermost fixed scroll.
  • the anti-rotation guide guides anti-rotation pins attached at two or more positions on the anti-rotation plate attached to the tip of the turning shaft.
  • the balance bearing guides the tip of the pivot shaft.
  • one end of the orbiting shaft is guided by the guide mechanism to perform the orbiting motion, so that a radial load acts on the orbiting shaft.
  • a load that cancels the load acting in the radial direction of the turning shaft is generated.
  • the orbiting scroll wrap and the fixed scroll lap contact each other to generate vibration noise, wear, or seizure. Do not do. Therefore, a highly reliable scroll fluid machine can be provided.
  • FIG. 1 shows a first embodiment.
  • FIG. 2 is a cross-sectional view taken along the line AA in FIG.
  • the anti-wrap surface of the first fixed scroll 1 having a spiral wrap is fixed to the casing 100 on the end plate.
  • a rotating scroll 10 having a spiral wrap is installed on the end plate so as to overlap the first fixed scroll 1
  • a second fixed scroll 2 having a spiral wrap is installed on the end plate so as to overlap the orbiting scroll 10, and the first fixed scroll. It is fixed to the scroll 1.
  • the first fixed scroll 1, the orbiting scroll 10 and the second fixed scroll 2 constitute an operating part.
  • the first fixed scroll wrap 1 a and the orbiting scroll wrap 10 a provided on the orbiting scroll 10 are combined to constitute a set of first working chambers 21.
  • the orbiting scroll wrap 10b provided on the orbiting scroll 10 and the second fixed scroll wrap 2a are combined to constitute a set of second working chambers 22.
  • the outer ring of the rotary bearing 101 is installed in the casing 100 at two locations.
  • a rotary shaft 102 is fitted to the inner ring of the rotary bearing 101.
  • a motor stator 105 is fixed to the casing 100, and a motor rotor 106 is fixed to the rotating shaft 102. Further, a balancer 47 for balancing the entire centrifugal force is attached to the rotating shaft 102.
  • the rotary shaft 102 is provided with bearing housings at both ends of the position eccentric from the rotation center, and the outer ring of the swivel bearing 103 is installed in the bearing housing.
  • a turning shaft 104 is fitted to the inner ring of the turning bearing 103. The turning shaft 104 passes through the first fixed scroll through hole 1c.
  • a hole is provided in the center of the orbiting scroll 10.
  • the hole is fitted to the turning drive unit 104a without relative rotation.
  • One end 104b of the turning shaft passes through the second fixed scroll through hole 2c and extends outward.
  • An anti-rotation plate 109 is fixed to one end 104b of the turning shaft.
  • anti-rotation pins 110 are embedded at three positions on the inner surface side of the anti-rotation plate 109.
  • An anti-rotation bearing (guide mechanism) 111 is installed on the front side of the second fixed scroll 2 as an anti-rotation guide.
  • the anti-rotation plate 109, the anti-rotation pin 110, and the anti-rotation bearing (guide mechanism) 111 constitute an anti-rotation means.
  • the anti-rotation pin 110 is combined in a state in contact with the anti-rotation bearing inner ring 112.
  • the outer diameter of the rotation prevention pin 110 is d1
  • the inner diameter of the rotation prevention bearing inner ring 112 is D1
  • the turning radius of the turning shaft 104 when the fluid machine is operated is ⁇
  • the bearing internal clearance is ⁇ , d1, D1
  • the following relationship is set between ⁇ and ⁇ . 2 ⁇ ⁇ D1 ⁇ d1 ⁇ 2 ⁇ + ⁇ (Formula 1)
  • the rotation prevention pin 110 is kept in contact with the rotation prevention bearing inner ring 112, and the rotation of the turning shaft 104 is reliably prevented. Further, the turning shaft one end 104b is not bent inward by a strong force.
  • the discharge cover 113 is fixed to the outer surface of the second fixed scroll 2 so as to seal the discharge chamber 114.
  • the discharge cover 113 includes a rotation prevention plate 109 and a rotation prevention bearing (guide mechanism) 111.
  • a discharge port 108 is provided in the discharge cover 113.
  • a suction port 107 is provided on the outer peripheral portion of the second fixed scroll 2.
  • a turning drive unit 104a which is a part of the turning shaft 104, drives the turning scroll 10 to turn.
  • a first working chamber 21 composed of the first fixed scroll wrap 1a and the orbiting scroll wrap 10a and a second working chamber 22 composed of the second fixed scroll wrap 2a and the orbiting scroll wrap 10b move from the outer peripheral side to the inner peripheral side. However, the volume is reduced and the internal fluid is compressed.
  • a revolving end plate communication port 10c is provided at the center of the end plate of the orbiting scroll 10.
  • the working chamber 21 and the working chamber 22 communicate with each other at the center.
  • the fluid is sucked from the suction port 107, compressed through the suction chamber 130, joined to the working chamber 22 side, flows into the discharge chamber 114 through the second fixed scroll through-hole 2 c, and is discharged to the discharge port 108. Discharged from the outside.
  • the rotation prevention pin 110 Since there is a relationship of Equation 1 between the outer diameter d1 of the rotation prevention pin 110 and the inner diameter D1 and the turning radius ⁇ of the rotation prevention bearing inner ring 112, the rotation prevention pin 110 always has a certain amount of space between the rotation prevention bearing inner ring 112 and the rotation prevention bearing inner ring 112. Swing motion while maintaining contact force. Since the anti-rotation plate 109 has the anti-rotation pins 110 at two or more places on the anti-rotation plate 109, the anti-rotation plate 109 rotates but cannot rotate. Since the rotation prevention plate 109 is fixed to the turning shaft one end 104b, the turning shaft 104 is turned and prevented from rotating. Further, since the orbiting scroll 10 is fitted to the orbiting drive unit 104a without being relatively rotated, the orbiting scroll 10 is prevented from rotating and is orbited.
  • the orbiting scroll 10 since the orbiting scroll 10 has a mass, a centrifugal force is generated in a direction perpendicular to the axis when the orbiting movement is performed. The entire centrifugal force is canceled by the balancer 47. However, the centrifugal force becomes a load that attempts to displace the orbiting scroll in the radial direction about the shaft. This load is a load for bending the turning drive unit 104a. The turning drive unit 104a bends in the direction of the combined load with the turning bearing 103 as a fulcrum. As a result, the orbiting scroll 10 is also displaced while being inclined in the direction of the combined load.
  • the orbiting scroll wraps 10a and 10b approach the first fixed scroll wrap 1a and the second fixed scroll wrap 2a. If the laps come too close, the gap between the laps, which was originally set to be small in order to suppress leakage, becomes zero, and sliding begins. Then, sliding loss occurs in the wrap. Further, vibration noise is generated in the scroll fluid machine. Furthermore, wear of the lap progresses, and seizure occurs between the laps. That is, both the performance and reliability of the scroll fluid machine are impaired.
  • the scroll fluid machine of the present invention can achieve a higher speed rotation than the conventional one even if it has a large orbiting scroll.
  • FIG. 3 is a partial sectional view showing a modification of the first embodiment.
  • a rotation preventing sliding member (guide mechanism) 115 is used instead of the rotation preventing bearing (guide mechanism) 111 as the rotation preventing guide.
  • the anti-rotation plate 109, the anti-rotation pin 110 and the anti-rotation sliding member (guide mechanism) 115 constitute an anti-rotation means.
  • the rotation preventing sliding member (guide mechanism) 115 is made of a self-lubricating member such as resin. Since the rotation prevention pin 110 is guided to make a turning motion while being inscribed in the inner surface of the rotation prevention sliding member (guide mechanism) 115, the rotation of the turning shaft 104 and the turning scroll 10 is prevented, and the turning shaft one end 104b is rotated. It cannot be displaced beyond the turning radius determined by the prevention pin 110 and the rotation prevention sliding member (guide mechanism) 115.
  • the rotation prevention pin 110 and the rotation prevention sliding member (guide mechanism) 115 are in contact with each other, the rotation of the orbiting scroll is reliably prevented. Even if the centrifugal force of the orbiting scroll 10 acts on the orbiting drive unit 104a, the orbiting shaft one end 104b does not bend after the rotation preventing pin 110 and the rotation preventing sliding member (guide mechanism) 115 are in contact with each other. Thereby, contact of laps can be prevented. Therefore, even if the scroll fluid machine according to the present invention has a large orbiting scroll, it can perform a revolving motion at a higher speed and with higher accuracy than the conventional one.
  • FIG. 4 shows another modification of the first embodiment.
  • FIG. 4 shows an example in which cooling is performed by providing a fan 31 at the rotating shaft rear end 102a when the first embodiment is a vacuum pump.
  • the bearing board 35 is provided with a vent hole 36 therethrough.
  • An exhaust port 34 is provided on the side surface of the casing 100 on the side closer to the first fixed scroll 1 than the stator 105.
  • the turning shaft 104 is provided with a turning shaft ventilation passage 32 penetrating therethrough.
  • the bottom plate 100a of the casing 100 has a hole, and the filter 30 is attached. When the fan 31 rotates together with the rotating shaft 102, air is taken in from the outside through the filter 30.
  • the air that has entered from the filter 30 passes through the vent 36 and passes through the motor space 33 in the casing 100 and is discharged to the outside from the exhaust 34. During this time, the rotary bearing 101 and the stator 105 are cooled, and an excessive temperature rise is prevented. Further, the air that has entered from the filter 30 exits the fan 31, flows into the discharge chamber 114 through the swirl shaft air passage 32, and is discharged along with the air discharged from the first working chamber 21 and the second working chamber 22. 108 is discharged to the outside. During this time, the central portions of the orbiting bearing 101 and the orbiting scroll 10 are cooled, and an excessive temperature rise is prevented.
  • FIG. 4 also shows an example in which a seal member for sealing the space on the working chamber side and the casing side is provided when the first embodiment of the present invention is a vacuum pump.
  • the ring-shaped inner surface seal 42 is attached so as to surround the first fixed scroll through hole 1c.
  • the seal plate 40 is attached to the pivot shaft 104 so as to contact the inner surface seal 42.
  • the seal cover 41 is attached to the casing side facing the seal plate 40.
  • the ring-shaped outer surface seal 43 is attached to the seal cover 41 and is in contact with the seal plate 40.
  • the discharged gas is blocked from the outside air by the discharge cover 113 and is exhausted through an external pipe (not shown) connected to the discharge port 108. Therefore, even if toxic gas or corrosive gas flows into the working chamber, it does not leak into the outside air.
  • FIG. 5 shows a second embodiment.
  • 6 is a cross-sectional view taken along the line AA in FIG.
  • the same parts as in the first embodiment use the same symbols and names, and the description thereof is omitted.
  • the discharge cover 113 is attached to the outer surface of the end plate of the second fixed scroll 2.
  • the balance bearing (guide mechanism) 51 is attached inside the discharge cover 113.
  • the outer peripheral surface of the turning shaft one end 104b turns while inscribed in the balance bearing inner ring 52.
  • the outer diameter of the pivot shaft end 104b is d2
  • the inner diameter of the balance bearing inner ring 52 is D2
  • the pivot radius of the pivot shaft 104 when the scroll fluid machine is operated is ⁇
  • the bearing internal clearance is ⁇ , d2, D2
  • the following relationship is set between ⁇ and ⁇ . 2 ⁇ ⁇ D2 ⁇ d2 ⁇ 2 ⁇ + ⁇ (Formula 2)
  • D1-d1 is set in this way, the swing shaft one end 104b is kept substantially in contact with the balance bearing inner ring 52. Further, the turning shaft one end 104b is not bent inward by a strong force. Therefore, no noise is generated and the mechanical loss is reduced.
  • the orbiting shaft end 104b does not bend any more when the bearing internal clearance of the balance bearing (guide mechanism) 51 becomes zero. Thereby, the contact of the scroll wrap can be prevented. Therefore, even if the scroll fluid machine has a large orbiting scroll, it can rotate at a higher speed than before.
  • the rotation prevention plate 60 is fixed to the other end 104c of the turning shaft.
  • the anti-rotation pins 61 are embedded at two or more locations on the anti-rotation plate 60.
  • the rotation prevention bearing 62 is attached to the bottom plate 100 a of the casing 100.
  • the rotation prevention pin 61 turns while inscribed in the rotation prevention bearing inner ring 63. If the outer diameter of the rotation prevention pin 61 is d3, the inner diameter of the rotation prevention bearing inner ring 63 is D3, the turning radius of the turning shaft 104 when the fluid machine is operated is ⁇ , and the bearing internal clearance is ⁇ , d3, D3, The following relationship is set between ⁇ and ⁇ .
  • FIG. 7 shows a modification of the second embodiment.
  • the turning shaft one end 104b has a barrel shape having a curved surface in the axial direction.
  • the swivel shaft one end 104b does not come into contact with the balance bearing inner ring 52. Therefore, galling and wear are less likely to occur on the surface where the pivot shaft end 104b and the balance bearing inner ring 52 come into contact. Therefore, the reliability of the scroll fluid machine is increased.
  • the anti-rotation sliding member 64 is used as a guide for the anti-rotation pin 61 attached to the anti-rotation plate 60.
  • the rotation preventing sliding member 64 is made of a self-lubricating member such as resin.
  • the rotation preventing sliding member 64 may be made of a wear-resistant surface-treated metal member.
  • FIG. 8 shows a third embodiment.
  • the cover 70 seals the outer surface of the center portion of the second fixed scroll 2 and blocks the working chamber side and the atmosphere side. Further, the discharge port 71 is provided on the bottom side of the stator 105 on the outer periphery of the casing 100.
  • the fluid flows in from the suction port 107, is compressed in the first working chamber 21 and the second working chamber 22, enters the casing 100 from the first fixed scroll through-hole 1 c, passes through the inside of the casing 100, and discharges 71. Discharged from the outside.
  • a simple cover 70 is sufficient instead of the discharge cover 113. Therefore, in the scroll fluid machine, one machining part can be reduced and the cost can be reduced. Further, since the protrusion is eliminated, the overall length can be shortened, and the inside of the casing can be cooled by the movement of the working fluid.
  • FIG. 9 shows a fourth embodiment.
  • the fluid machine shown in FIG. 9 is a twin-type scroll fluid machine having scrolls at both ends of the turning shaft 104.
  • the anti-wrap surface of the first fixed scroll 1 is fixed to the right side of the casing 100.
  • a first orbiting scroll 11 is installed on the first fixed scroll 1.
  • a second fixed scroll 2 is installed over the first orbiting scroll 11 and is fixed to the first fixed scroll 1.
  • the first fixed scroll 1, the first orbiting scroll 11 and the second fixed scroll 2 constitute an orbiting shaft one end side operating portion.
  • the first fixed scroll wrap 1a and the first orbiting scroll wrap 11a are combined to constitute a set of first working chambers 21.
  • the first orbiting scroll wrap 11b and the second fixed scroll wrap 2a are combined to constitute a set of second working chambers 22.
  • a first orbiting end plate communication port 11 c is provided in the center portion of the end plate of the first orbiting scroll 11.
  • the first working chamber 21 joins the second working chamber 22 through the first swivel end plate communication port 11c.
  • the fluid is sucked from the first suction port 107a, is compressed through the first suction chamber 131, merges into the working chamber 22 side, passes through the second fixed scroll through-hole 2c, and enters the first discharge cover 113a.
  • the anti-wrap surface of the third fixed scroll 3 is fixed to the left side of the casing 100.
  • a second orbiting scroll 12 is installed on the third fixed scroll 3.
  • a fourth fixed scroll 4 is installed on the second orbiting scroll 12 and is fixed to the third fixed scroll 3.
  • the third fixed scroll 3, the second orbiting scroll 12 and the fourth fixed scroll 4 constitute an orbiting shaft other end side operation portion.
  • the third fixed scroll wrap 3a and the second orbiting scroll wrap 12a are combined to constitute a set of third working chambers 23.
  • the second orbiting scroll wrap 12b and the fourth fixed scroll wrap 4a are combined to constitute a set of fourth working chambers 24.
  • the rotating shaft 102 rotates, and the turning shaft 104 is prevented from rotating and driven eccentrically.
  • a second turning drive unit 104 d that is a part of the turning shaft 104 drives the turning scroll 12 to turn.
  • the working fluid moves from the outer peripheral side to the inner peripheral side of the third working chamber 23 and the fourth working chamber 24, the volume is reduced, and the working fluid is compressed.
  • a second orbiting end plate communication port 12 c is provided at the center of the end plate of the second orbiting scroll 12.
  • the third working chamber 23 merges with the fourth working chamber 24 through the second swivel end plate communication port 12c.
  • the working fluid sucked from the second suction port 107b is compressed via the second suction chamber 132, passes through the fourth fixed scroll through-hole 4c, and the second discharge chamber 114b in the second discharge cover 113b. And is discharged from the second discharge port 108b to the outside.
  • the outer ring of the rotary bearing 101 is installed in the casing 100 at two locations.
  • a rotary shaft 102 is fitted to the inner ring of the rotary bearing 101.
  • a balancer 47 for balancing the entire centrifugal force is attached to the rotary shaft 102 at two locations.
  • a motor stator 105 is fixed to the casing 100, and a motor rotor 106 is fixed to the rotating shaft 102. Further, a balancer 47 for balancing the entire centrifugal force is attached to the rotating shaft 102.
  • the rotary shaft 102 is provided with bearing housings at both ends of the position eccentric from the rotation center, and the outer ring of the swivel bearing 103 is installed in the bearing housing.
  • a turning shaft 104 is fitted to the inner ring of the turning bearing 103.
  • the turning shaft 104 passes through the first fixed scroll through hole 1c.
  • a hole is provided in the center of the first orbiting scroll 11.
  • the hole is fitted to the turning drive unit 104a so as not to rotate relatively.
  • One end 104b of the turning shaft passes through the second fixed scroll through hole 2c and extends outward.
  • the rotation prevention plate 109 is fixed to the turning shaft one end 104b.
  • the rotation prevention pins 110 are embedded at three locations on the inner surface side of the rotation prevention plate 109.
  • An anti-rotation bearing (guide mechanism) 111 is installed on the front side of the second fixed scroll 2.
  • the anti-rotation pin 110 is combined in a state in contact with the anti-rotation bearing inner ring 112.
  • the outer diameter of the rotation prevention pin 110 is d1
  • the inner diameter of the rotation prevention bearing inner ring 112 is D1
  • the turning radius of the turning shaft 104 when the fluid machine is operated is ⁇
  • the bearing internal clearance is ⁇ , d1, D1, ⁇ and ⁇ are set so as to have the relationship of Equation 1.
  • the turning shaft 104 passes through the third fixed scroll through hole 3c.
  • a hole is provided in the center of the second orbiting scroll 12.
  • the hole is fitted to the second turning drive unit 104d in a state where it does not rotate relative to the second turning drive unit 104d.
  • the other end 104c of the turning shaft passes through the fourth fixed scroll through hole 4c and extends to the outside.
  • the bearing block 50 is attached to the outer surface of the end plate of the fourth fixed scroll 4.
  • the balance bearing (guide mechanism) 51 is attached inside the bearing block 50.
  • the outer peripheral surface of the other end 104c of the turning shaft makes a turning motion while being inscribed in the balance bearing inner ring 52.
  • one set of scroll portions is provided on one side of the casing 100, and another set of scroll portions is provided on the opposite side of the casing 100. Therefore, in this embodiment, it is possible to produce a flow rate twice that of a fluid machine in which one set of scroll portions is provided on one side of the casing 100.
  • An anti-rotation mechanism is provided at the turning shaft end 104 b on the right side of the turning shaft 104. Further, there is a relationship of Formula 1 between the outer diameter of the rotation prevention pin 110 and the inner diameter of the rotation prevention bearing inner ring 112. Therefore, the rotation of the turning shaft 104 is reliably prevented. Further, bending of the turning shaft one end 104b due to centrifugal force is prevented.
  • the outer peripheral surface of the other end 104c of the turning shaft makes a turning motion while being inscribed in the balance bearing inner ring 52. Further, there is a relationship of Formula 2 between the other end of the turning shaft 104 c and the balance bearing inner ring 52. Therefore, bending of the other end 104c of the turning shaft due to centrifugal force is prevented.
  • FIG. 10 shows a fifth embodiment.
  • the structure of the drive unit is the same as that of the fourth embodiment.
  • the same parts as those in the fourth embodiment use the same symbols and names, and the description thereof is omitted.
  • the difference between this embodiment and the fourth embodiment will be described.
  • One end 104b of the turning shaft passes through the second fixed scroll through hole 2c and extends outward.
  • a first discharge cover 113 a is attached to the outer surface of the end plate of the second fixed scroll 2.
  • a first balance bearing (guide mechanism) 51a is attached to the inside of the first discharge cover 113a.
  • the outer peripheral surface of the turning shaft one end 104b turns while inscribed in the first balance bearing inner ring 52a.
  • the outer diameter of the turning shaft one end 104b is d2
  • the inner diameter of the first balance bearing inner ring 52a is D2
  • the turning radius of the turning shaft 104 when the fluid machine is operated is ⁇
  • the bearing internal clearance is ⁇ , d2, D2 , ⁇ , and ⁇ are set so as to satisfy the relationship of Equation 2.
  • the second discharge cover 113 b is attached to the outer surface of the end plate of the fourth fixed scroll 4.
  • a second balance bearing (guide mechanism) 51b is attached inside the second discharge cover 113b.
  • the outer peripheral surface of the other end 104c of the turning shaft makes a turning motion while being inscribed in the second balance bearing inner ring 52b. If the outer diameter of the other end 104c of the swing shaft is d2, the inner diameter of the second balance bearing inner ring 52b is D2, the swing radius of the swing shaft 104 when the fluid machine is operated is ⁇ , and the internal clearance of the bearing is ⁇ , d2 D2, ⁇ , and ⁇ are set so as to satisfy the relationship of Equation 2.
  • the rotation prevention plate 60 is attached between the right side of the slewing bearing 103 and the end plate of the first fixed scroll 1 so as not to rotate relatively.
  • Anti-rotation pins 61 are embedded at three locations on the outer periphery of the anti-rotation plate.
  • An anti-rotation bearing 62 is installed on the end plate of the first fixed scroll 1.
  • the rotation prevention pin 61 turns while inscribed in the rotation prevention bearing inner ring 63.
  • the outer diameter of the rotation prevention pin 61 is d3
  • the inner diameter of the rotation prevention bearing inner ring 63 is D3
  • the turning radius of the turning shaft 104 when the fluid machine is operated is ⁇
  • the bearing internal clearance is ⁇ , d3, D3, ⁇ and ⁇ are set so as to have the relationship of Equation 3.
  • one set of scroll portions is provided on one side of the casing 100, and one set of scroll portions is provided on the other side of the casing 100. Accordingly, in this embodiment, as in the fourth embodiment of the present invention, a flow rate twice that of a fluid machine in which one set of scroll portions is provided on one side of the casing 100 can be obtained.
  • the outer peripheral surface of the turning shaft one end 104b turns while inscribed in the first balance bearing inner ring 52a. There is a relationship of Formula 2 between the turning shaft one end 104b and the first balance bearing inner ring 52a. Therefore, bending of the turning shaft one end 104b due to centrifugal force is prevented.
  • the outer peripheral surface of the other end 104c of the turning shaft makes a turning motion while being inscribed in the second balance bearing inner ring 52b.
  • Formula 2 also between the other end 104c of the turning shaft and the second balance bearing inner ring 52b. Therefore, the bending of the other end 104c of the turning shaft due to the centrifugal force is prevented.
  • FIG. 11 shows a sixth embodiment.
  • the outer surface of the center portion of the second fixed scroll 2 is covered with a first cover 70a to block the working chamber side and the atmosphere side.
  • the outer surface of the central portion of the fourth fixed scroll 4 is covered with a second cover 70b to block the working chamber side and the atmosphere side.
  • the discharge port 71 is provided in a part of the side surface of the casing 100.
  • the fluid that has exited the first working chamber 21 and the second working chamber 22 enters the casing 100 through the first fixed scroll through hole 1c.
  • the fluid that has exited the third working chamber 23 and the fourth working chamber 24 enters the casing 100 through the third through-hole 3c.
  • the fluid that has entered the casing 100 passes through the inside of the casing 100 and is discharged from the discharge port 71 to the outside.
  • simple first cover 70a and second cover 70b are sufficient as shown in FIG. 11, so that it is not necessary to use first discharge cover 113a and second discharge cover 113b as shown in FIG. Therefore, with this structure, two processed parts can be reduced, the cost can be reduced, and the total length can be shortened because there are no protrusions. Further, the inside of the casing can be cooled with the compressed working fluid.
  • FIG. 12 shows a seventh embodiment.
  • FIG. 12 shows a fluid machine having two sets of scroll units in the turning drive unit 104a. The same components as those in the first embodiment are denoted by the same symbols and names, and the description thereof is omitted.
  • the anti-wrap surface of the first fixed scroll 1 is fixed to the casing 100.
  • a first orbiting scroll 11 is placed over the first fixed scroll 1.
  • the third fixed scroll 3 is installed on the first orbiting scroll 11 and is fixed to the first fixed scroll 1.
  • a second orbiting scroll 12 is placed over the third fixed scroll 3.
  • the second fixed scroll 2 is installed over the second orbiting scroll 12 and is fixed to the first fixed scroll 1 together with the third fixed scroll 3.
  • the first fixed scroll 1, the first orbiting scroll 11, the third fixed scroll 3, the second orbiting scroll 12, and the second fixed scroll 2 constitute an operating unit.
  • One set of first working chambers 21 is constituted by a combination of a first fixed scroll wrap 1a and a first orbiting scroll wrap 11a.
  • One set of the second working chamber 22 is configured by a combination of the first orbiting scroll wrap 11b and the third fixed scroll wrap 3a.
  • One set of the third working chamber 23 is configured by a combination of the third fixed scroll wrap 3b and the second orbiting scroll wrap 12a.
  • One set of fourth working chambers 24 is constituted by a combination of the second orbiting scroll wrap 12b and the second fixed scroll wrap 2a.
  • the third fixed scroll suction communication port 3d is provided in the third fixed scroll 3, the first suction chamber 131 and the second suction chamber 132 are in communication.
  • a first orbiting end plate communication port 11 c is provided in the center portion of the end plate of the first orbiting scroll 11.
  • the first working chamber 21 joins the second working chamber 22 through the first swivel end plate communication port 11c.
  • a second orbiting end plate communication port 12 c is provided at the center of the end plate of the second orbiting scroll 12.
  • the third working chamber 23 joins the fourth working chamber 24 through the second swivel end plate communication port 12c. Therefore, the fluid is sucked into all the working chambers from the suction port 107 and discharged from the discharge port 108 to the outside.
  • the turning shaft 104 passes through the first fixed scroll through hole 1c.
  • a hole is provided in the center of the first orbiting scroll 11.
  • the hole is fitted to the turning drive unit 104a so as not to rotate relatively.
  • the turning shaft 104 passes through the third fixed scroll through hole 3c.
  • a hole is also provided in the center of the second orbiting scroll 12.
  • the hole is fitted to the turning drive unit 104a so as not to rotate relatively.
  • One end 104b of the turning shaft passes through the second fixed scroll through hole 2c and extends outward.
  • a discharge cover 113 is attached to the outer surface of the end plate of the second fixed scroll 2.
  • a balance bearing (guide mechanism) 51 is attached inside the bearing discharge cover 113.
  • the outer peripheral surface of the turning shaft one end 104b turns while inscribed in the balance bearing inner ring 52.
  • the outer diameter of the pivot shaft end 104b is d2
  • the inner diameter of the balance bearing inner ring 52 is D2
  • the pivot radius of the pivot shaft 104 when the fluid machine is operated is ⁇
  • the bearing internal clearance is ⁇ , d2, D2, ⁇ , ⁇
  • a rotation prevention mechanism similar to that of the second embodiment is incorporated in the other end 104c of the turning shaft.
  • An anti-rotation bearing 62 is mounted on the bottom plate 100a. The anti-rotation pin 61 is kept in contact with the inner ring 63 of the anti-rotation bearing. Therefore, the rotation of the turning shaft 104 is reliably prevented.
  • the swivel shaft one end 104b and the balance bearing inner ring 52 are kept substantially in contact with each other.
  • the turning shaft one end 104b does not bend any more when the bearing internal clearance of the balance bearing inner ring 52 becomes zero. Therefore, contact between laps is prevented.
  • the scroll fluid machine has a large orbiting scroll, it can rotate at a higher speed than before.
  • a flow rate twice that of a fluid machine in which one set of scroll portions is provided on one side of the casing 100 can be obtained.
  • FIG. 13 and 14 show an example in which the phases of suction and discharge are shifted in the seventh embodiment.
  • the scroll fluid machine can change the suction and discharge phases with respect to the eccentric direction of the orbiting shaft by changing the rotational direction position of the lap during assembly.
  • the first fixed scroll wrap 1a and the first orbiting scroll wrap 11a, the third fixed scroll wrap 3a and the first orbiting scroll wrap 11b, the third fixed scroll wrap 3b and the second orbiting scroll wrap 12a In the combination of the two fixed scroll wrap 2a and the second orbiting scroll wrap 12b, the lap phase is rotated by 90 degrees.
  • first orbiting scroll wrap 11a the first orbiting scroll wrap 11b, the second orbiting scroll wrap 12a, and the second orbiting scroll wrap 12b are all eccentric in the same direction (the right side in the drawing), 4 The phases of the two working chambers are shifted by 90 degrees.
  • FIG. 15 shows an eighth embodiment.
  • the same components as those in the first embodiment are denoted by the same symbols and names, and the description thereof is omitted.
  • the anti-wrap surface of the first fixed scroll 1 is fixed to the right side of the casing 100.
  • a first orbiting scroll 11 is placed over the first fixed scroll 1.
  • the third fixed scroll 3 is installed on the first orbiting scroll 11 and is fixed to the first fixed scroll 1.
  • a second orbiting scroll 12 is placed over the third fixed scroll 3.
  • the second fixed scroll 2 is installed over the second orbiting scroll 12 and is fixed to the first fixed scroll 1 together with the third fixed scroll 3.
  • the first fixed scroll 1, the first orbiting scroll 11, the third fixed scroll 3, the second orbiting scroll 12, and the second fixed scroll 2 constitute an orbiting shaft one end side operating portion.
  • One set of first working chambers 21 is constituted by a combination of a first fixed scroll wrap 1a and a first orbiting scroll wrap 11a.
  • One set of the second working chamber 22 is configured by a combination of the first orbiting scroll wrap 11b and the third fixed scroll wrap 3a.
  • a first orbiting end plate communication port 11 c is provided in the center portion of the end plate of the first orbiting scroll 11.
  • the first working chamber 21 joins the second working chamber 22 through the first swivel end plate communication port 11c.
  • One set of the third working chamber 23 is configured by a combination of the third fixed scroll wrap 3b and the second orbiting scroll wrap 12a.
  • One set of fourth working chambers 24 is constituted by a combination of the second orbiting scroll wrap 12b and the second fixed scroll wrap 2a.
  • a second orbiting end plate communication port 12 c is provided at the center of the end plate of the second orbiting scroll 12.
  • the third working chamber 23 joins the fourth working chamber 24 through the second swivel end plate communication port 12c. Since the third fixed scroll suction communication port 3d is provided in the third fixed scroll 3, the first suction chamber 131 and the second suction chamber 132 are in communication. Further, since the third fixed scroll through-hole 3c is provided at the center of the third fixed scroll 3, the fluid sucked from the first suction port 107a is compressed in the working chambers 21, 22, 23, 24, They gather in the discharge chamber 114 in the first discharge cover 113a and are discharged from the first discharge port 108a to the outside.
  • the anti-wrap surface of the fourth fixed scroll 4 is fixed to the left side of the casing 100.
  • a third orbiting scroll 13 is installed on the fourth fixed scroll 4.
  • the sixth fixed scroll 6 is installed on the third orbiting scroll 13 and is fixed to the fourth fixed scroll 4.
  • a fourth orbiting scroll 14 is installed so as to overlap the sixth fixed scroll 6.
  • the fifth fixed scroll 5 is placed on the fourth orbiting scroll 14 and is fixed to the fourth fixed scroll 4 together with the sixth fixed scroll 6.
  • the fourth fixed scroll 4, the third orbiting scroll 13, the sixth fixed scroll 6, the fourth orbiting scroll 14 and the fifth fixed scroll 5 constitute an orbiting shaft other end side operation portion.
  • One set of fifth working chambers 25 is constituted by a combination of the fourth fixed scroll wrap 4a and the third orbiting scroll wrap 13a.
  • One set of sixth working chambers 26 is configured by a combination of the third orbiting scroll wrap 13b and the sixth fixed scroll wrap 6a.
  • a third orbiting end plate communication port 13 c is provided at the center of the end plate of the third orbiting scroll 13.
  • the fifth working chamber 25 joins the sixth working chamber 26 through the third swivel end plate communication port 13c.
  • One set of seventh working chambers 27 is constituted by a combination of a sixth fixed scroll wrap 6b and a fourth orbiting scroll wrap 14a.
  • One set of eighth working chambers 28 is configured by a combination of the fourth orbiting scroll wrap 14b and the fifth fixed scroll wrap 5a.
  • a fourth orbiting end plate communication port 14 c is provided at the center of the end plate of the fourth orbiting scroll 14.
  • the seventh working chamber 27 joins the eighth working chamber 28 through the fourth swivel end plate communication port 14c.
  • the sixth fixed scroll suction communication port 6d is provided in the sixth fixed scroll 6, the third suction chamber 133 and the fourth suction chamber 134 are in communication.
  • the sixth fixed scroll through-hole 6c is provided at the center of the sixth fixed scroll 6, the fluid sucked from the second suction port 107b is compressed in the working chambers 25, 26, 27, and 28, The ink is discharged to the outside from the second discharge port 108b provided in the second discharge cover 113b.
  • the structure of the drive unit is the same as in the first embodiment.
  • the turning shaft 104 passes through the first fixed scroll through hole 1c.
  • a hole is provided in the center of the first orbiting scroll 11 and the second orbiting scroll 12. The hole is fitted to the turning drive unit 104a so as not to rotate relatively.
  • One end 104b of the turning shaft passes through the second fixed scroll through hole 2c and extends outward.
  • An anti-rotation plate 109 is fixed to one end 104b of the turning shaft. As shown in FIG. 2, the anti-rotation pins 110 are embedded at three locations on the inner surface side of the anti-rotation plate 109.
  • An anti-rotation bearing (guide mechanism) 111 is installed on the front side of the second fixed scroll 2 as an anti-rotation guide.
  • the anti-rotation plate 109, the anti-rotation pin 110, and the anti-rotation bearing (guide mechanism) 111 constitute an anti-rotation means.
  • the anti-rotation pin 110 is combined in a state in contact with the anti-rotation bearing inner ring 112. If the outer diameter of the rotation prevention pin 110 is d1, the inner diameter of the rotation prevention bearing inner ring 112 is D1, the turning radius of the turning shaft 104 when the fluid machine is operated is ⁇ , and the bearing internal clearance is ⁇ , d1, D1, ⁇ and ⁇ are set so as to have the relationship of Equation 1.
  • the turning shaft 104 passes through the fourth fixed scroll through hole 4c.
  • a hole is provided at the center of the third orbiting scroll 13 and the fourth orbiting scroll 14. The hole is fitted to the second turning drive unit 104d in a state where it does not rotate relative to the second turning drive unit 104d.
  • the other end 104c of the turning shaft passes through the fifth fixed scroll through hole 5c and extends to the outside.
  • a second discharge cover 113 b is attached to the outer surface of the end plate of the fifth fixed scroll 5.
  • a balance bearing (guide mechanism) 51 is attached inside the second discharge cover 113b.
  • the outer peripheral surface of the other end 104c of the turning shaft makes a turning motion while being inscribed in the balance bearing inner ring 52.
  • Equation 2 If the outer diameter of the other end 104c of the rotating shaft is d2, the inner diameter of the balance bearing inner ring 52 is D2, the turning radius of the rotating shaft 104 when the fluid machine is operated is ⁇ , and the internal clearance of the bearing is ⁇ , d2, D2, ⁇ and ⁇ are set so as to have the relationship of Equation 2.
  • the rotation prevention means provided at the turning shaft end 104b on the right side of the turning shaft 104 reliably prevents the turning shaft 104 from rotating. Further, bending of the turning shaft one end 104b due to centrifugal force is prevented.
  • the outer peripheral surface of the other end 104c of the turning shaft makes a turning motion while being inscribed in the balance bearing inner ring 52. There is a relationship of Formula 2 between the other end 104 c of the turning shaft and the balance bearing inner ring 52. Therefore, the bending of the other end 104c of the turning shaft due to the centrifugal force is prevented.
  • FIG. 16 shows a modification of the eighth embodiment.
  • the structure of the drive unit is the same as in the eighth embodiment.
  • the same parts as those in the eighth embodiment use the same symbols and names, and the description thereof is omitted.
  • the difference between the present embodiment and the eighth embodiment will be described.
  • One end 104b of the turning shaft passes through the second fixed scroll through hole 2c and extends outward.
  • a first discharge cover 113 a is attached to the outer surface of the end plate of the second fixed scroll 2.
  • a first balance bearing (guide mechanism) 51a is attached to the inside of the first discharge cover 113a.
  • the outer peripheral surface of the turning shaft one end 104b makes a turning motion while being inscribed in the balance bearing inner ring 52a.
  • the outer diameter of the pivot shaft one end 104b is d2
  • the inner diameter of the balance bearing inner ring 52a is D2
  • the pivot radius of the pivot shaft 104 when the fluid machine is operated is ⁇
  • the bearing internal clearance is ⁇ , d2, D2, ⁇ , ⁇ are set so as to satisfy the relationship of Equation 2. Therefore, bending of the turning shaft one end 104b due to centrifugal force is prevented.
  • the other end 104c of the turning shaft passes through the fifth fixed scroll through hole 5c and extends to the outside.
  • a second discharge cover 113 b is attached to the outer surface of the end plate of the second fixed scroll 2.
  • a second balance bearing (guide mechanism) 51b is attached inside the second discharge cover 113b.
  • the outer peripheral surface of the other end 104c of the turning shaft makes a turning motion while being inscribed in the second balance bearing inner ring 52b.
  • Formula 2 also between the other end 104c of the turning shaft and the second balance bearing inner ring 52b. Therefore, the bending by the centrifugal force of the other end 104c of a turning shaft is prevented.
  • the rotation prevention plate 60 is attached between the right side of the slewing bearing 103 and the end plate of the first fixed scroll 1 so as not to rotate relatively.
  • Anti-rotation pins 61 are embedded at three locations on the outer periphery of the anti-rotation plate 60.
  • An anti-rotation bearing 62 is installed on the end plate of the first fixed scroll 1.
  • the anti-rotation plate 60, the anti-rotation pin 61 and the anti-rotation bearing 62 constitute an anti-rotation means.
  • the rotation prevention pin 61 turns while inscribed in the rotation prevention bearing inner ring 63.
  • a flow rate four times that of a fluid machine in which one set of scroll portions is provided on one side of the casing 100 can be produced as in the eighth embodiment of the present invention.
  • FIG. 17 shows a ninth embodiment.
  • the same parts as those in the seventh embodiment use the same symbols and names, and the description thereof is omitted.
  • the third fixed scroll 3 is divided into two.
  • the third fixed scroll first end plate 3e and the third fixed scroll second end plate 3f are integrated in close contact with each other.
  • a space is provided in the center of the third fixed scroll first end plate 3e and the third fixed scroll second end plate 3f.
  • a seal plate 44 fixed to the turning drive unit 104a is slidably sandwiched.
  • the first seal 45 attached to the third fixed scroll first end plate 3e and the second seal 46 attached to the third fixed scroll second end plate 3f seal both surfaces of the seal plate 44.
  • the third fixed scroll through-hole 3c is blocked in the middle by this seal.
  • the first working chamber 21 and the second working chamber 22 formed by a combination of the first fixed scroll wrap 1a, the first orbiting scroll wrap 11a, 11b, and the third fixed scroll wrap 3a constitute a compressor.
  • the third working chamber 23 and the fourth working chamber 24, which are a combination of the third fixed scroll wrap 3b, the second orbiting scroll wrap 12a, 12b, and the second fixed scroll wrap 2a, constitute an expander.
  • the discharge cover 113 provided on the second fixed scroll 2 is provided with an expander inlet 207b, and the working fluid flows in.
  • the working fluid enters the center of the fourth working chamber 24 from the second fixed scroll through-hole 2c, enters the third working chamber 23 from the second swivel end plate communication port 12c, and expands while moving toward the outer periphery. At this time, the working fluid gives a turning force to the second orbiting scroll 12.
  • An expander outlet 208 b is provided on the outer peripheral portion of the second fixed scroll 2.
  • the expanded working fluid is discharged from the expander outlet 208b.
  • a compressor suction port 207 a is provided on the outer peripheral portion of the first fixed scroll 1.
  • the inlet of the cooler (hot water heater) 121 is connected to the expander outlet 208b, and the outlet is connected to the compressor suction port 207a.
  • the working fluid cooled to the low temperature by the cooler 121 enters the first working chamber 21 and the second working chamber 22 from the compressor suction port 207a, and is compressed while moving toward the inner periphery.
  • the compressed working fluid joins through the first swivel end plate communication port 11c, enters the casing 100 through the first fixed scroll through-hole 1c, and is discharged to the outside from the compressor discharge port 208a.
  • the inlet of the heater (heat collector) 120 is connected to the compressor discharge port 208a, and the outlet is connected to the expander inlet 207b.
  • the working fluid exiting the compressor discharge port 208a is heated by the heater 120 and becomes high temperature, and flows into the expander from the expander inlet 207b. In this stroke, the work of the expander becomes larger than the power of the compressor, and the expander drives the compressor.
  • the expander further drives the turning drive unit 104a to drive the turning shaft 104 eccentrically.
  • the turning shaft 104 rotates the rotating shaft 102.
  • the rotating shaft 102 rotates the mounted rotor 105 to generate an electromotive force in the winding of the stator 106. As a result, electric power can be extracted from the winding. That is, this fluid machine becomes a generator.
  • the expander and the compressor are mounted on the same turning drive unit 104a, so that the power is transmitted as a load and no loss occurs between the expander and the compressor.
  • the working fluid is preferably a stable gas that does not liquefy at room temperature, such as air, nitrogen, or helium.
  • FIG. 18 shows a tenth embodiment.
  • two sets out of four working chambers are used as an expander and the other two sets are used as blowers, and applied to a fuel cell system. Is shown.
  • a blower inlet 307 is provided on the outer periphery of the first fixed scroll 1. Air enters the first working chamber 21 and the second working chamber 22 from the blower suction port 307 and is compressed while moving toward the inner periphery. The compressed air enters the casing 100 through the first fixed scroll through-hole 1c and is discharged to the outside through the blower discharge port 308.
  • An expander inlet 207 b is provided at the center of the second fixed scroll 2. The inlet of the fuel cell 122 is connected to the blower outlet 308, and the outlet is connected to the expander inlet 207b.
  • the exhaust air leaving the fuel cell 122 is still kept at a certain high pressure, enters the center of the third working chamber 23 and the fourth working chamber 24 from the second fixed scroll through-hole 2c, and expands while moving toward the outer periphery. . At this time, the air gives a turning force to the second turning scroll 12.
  • An expander outlet 208 b is provided on the outer peripheral portion of the second fixed scroll 2. The expanded air is discharged from the expander outlet 208b. In this process, the work of the expander supplements the power for driving the first orbiting scroll 11 of the blower, and energy is regenerated as the entire fuel cell system.
  • FIG. 19 shows a modification of the tenth embodiment.
  • FIG. 19 shows a fuel cell system in which a scroll fluid machine having the same structure as that of FIG. 15 is used by using four of the eight working chambers as an expander and the other four working chambers as blowers. An example applied to is shown.
  • a blower inlet 307 is provided on the outer periphery of the fifth fixed scroll 5. Air enters the fifth working chamber 25, the sixth working chamber 26, the seventh working chamber 27, and the eighth working chamber 28 from the blower suction port 307, and is compressed while moving toward the inner periphery. The compressed air passes through the fifth fixed scroll through hole 5c and is discharged to the outside from the blower discharge port 308 provided in the second discharge cover 113b.
  • An expander inlet 207b is provided at the center of the first discharge cover 113a installed on the second fixed scroll 2. The inlet of the fuel cell 122 is connected to the blower discharge port 308, and the outlet is connected to the expander inlet 207b.
  • the exhaust air leaving the fuel cell 122 is still kept at a high pressure to some extent, and the center of the fourth working chamber 24, the third working chamber 23, the second working chamber 22, and the first working chamber 21 from the second fixed scroll through hole 2c. Enters and expands while moving toward the outer periphery. At this time, the air gives a turning force to the first orbiting scroll 11 and the second orbiting scroll 12.
  • An expander outlet 208 b is provided on the outer peripheral portion of the second fixed scroll 2. The expanded air is discharged from the expander outlet 208b. In this stroke, the work of the expander supplements the power for driving the third or fourth scroll 13 and 14 of the blower, and energy is regenerated as the entire fuel cell system.
  • FIG. 20 shows a modification of the ninth or tenth embodiment.
  • a heat insulating plate 3g is sandwiched between the third fixed scroll first end plate 3e and the third fixed scroll second end plate 3f.
  • the power generated by the expander is increased by supplying a fluid as hot as possible.
  • the power consumption of the compressor is reduced when the fluid as low as possible is sucked. Therefore, as high a fluid as possible heated by the heater 120 is caused to flow into the working chambers 23 and 24 through the expander inlet 207b and the second fixed scroll through-hole 2c.
  • the low-temperature fluid sufficiently cooled by the cooler 121 is caused to flow into the working chambers 21 and 22 through the compressor suction port 207a.
  • the first fixed scroll 1, the first orbiting scroll 11, the third fixed scroll wrap 3a, and the third fixed scroll first end plate 3e of the compressor are relatively low in temperature.
  • the second fixed scroll 2, the second orbiting scroll 12, the third fixed scroll wrap 3b, and the third fixed scroll second end plate 3f of the expander become relatively hot.
  • the third fixed scroll wrap 3a cannot maintain a low temperature and the power consumption of the compressor.
  • the third fixed scroll wrap 3b cannot maintain a high temperature, and the power generated by the expander decreases. That is, the amount of power generation that can be taken out as a power difference between the expander and the compressor decreases.
  • the heat insulating plate 3g is sandwiched between the third fixed scroll first end plate 3e of the compressor and the third fixed scroll second end plate 3f of the expander, and the amount of heat transfer due to heat conduction therebetween is reduced. Yes. In this way, the power generation amount that can be taken out as the power difference between the expander and the compressor does not decrease.
  • FIG. 21 shows an eleventh embodiment. Components identical to those of the second embodiment are denoted by the same symbols and names, and description thereof is omitted.
  • a discharge cover 113 is attached to the outer surface of the end plate of the second fixed scroll 2.
  • a balance bearing (guide mechanism) 51 is attached inside the discharge cover 113.
  • a rotating cylinder 80 is integrally attached to the balance bearing inner ring 52.
  • a fan shaft 81 is integrally attached to the rotating cylinder 80.
  • a fan 82 is attached to the fan shaft 81.
  • the outer peripheral surface of the turning shaft end 104 b makes a turning motion while being inscribed in the inner surface of the rotating cylinder 80.
  • the rotating cylinder 80 rotates with the balance bearing inner ring 52, the fan shaft 81 also rotates, and the fan 82 rotates.
  • the rotary cylinder 80 is sealed on the inside and outside by a seal ring 83 attached to the discharge cover 113. Therefore, in the case of the compressor, the fluid is sucked from the suction port 107, compressed in the first working chamber 21 and the second working chamber 22, flows into the casing 100 through the first fixed scroll through-hole 1c, and is discharged. It is discharged from the outlet 108 to the outside.
  • the fan 82 rotates, outside air is taken in from the intake port 84 and blown to the outer surface of the second fixed scroll 2, and after cooling the second fixed scroll 2, the outside air is discharged from the exhaust port 85.
  • the fan 82 can be rotated by the turning motion of the turning shaft 104 without a special drive device such as an electric motor, and the second fixed scroll 2 can be cooled. Therefore, the number of parts of the scroll fluid machine is reduced, and the cost can be reduced.
  • the cross sections of the turning drive unit 104a and the second turning drive unit 104d are non-circular.
  • the holes formed in the centers of the orbiting scroll 10 and the first to fourth orbiting scrolls 11, 12, 13, and 14 that fit with the orbiting drive unit 104a and the second orbiting drive unit 104d have a similar non-circular shape.
  • the cross-section of the orbiting drive unit and the orbiting scroll hole have a triangular curved surface shape in the example of FIG. 22, a circular shape partially having a plane cut in the example of FIG. 23, and a rectangular shape in the example of FIG. ing.
  • the orbiting drive unit 104a, the second orbiting drive unit 104d and the orbiting scroll do not rotate relatively. Therefore, if the rotation of the orbiting shaft 104 is prevented, the rotation of the orbiting scrolls 10, 11, 12, 13, and 14 is also prevented.
  • the fit between the orbiting drive 104a or the second orbiting drive 104d and the orbiting scroll hole is a clearance fit. Therefore, the orbiting scrolls 10, 11, 12, 13, and 14 can move in the axial direction on the orbiting drive unit 104a and the second orbiting drive unit 104d. Therefore, even if the orbiting shaft 104 changes its dimensions due to thermal expansion, the orbiting scrolls 10, 11, 12, 13, and 14 do not receive a load in the axial direction.
  • the orbiting scrolls 10, 11, 12, 13, and 14 are positioned by being pinched by the fixed scroll with a slight gap between the tip of each lap and the end plate surface. Therefore, an excessive force is not generated at the wrap tip, and loss, wear, galling, and the like due to friction at the wrap tip can be prevented.
  • FIGS. 25 and 26 show a twelfth embodiment.
  • a self-lubricating cylindrical member 116 is attached to the rotation prevention bearing inner ring 112.
  • the rotation prevention pin 110 rotates while inscribed in the cylindrical member 116.
  • the outer diameter of the rotation prevention pin 110 is d1
  • the inner diameter of the cylindrical member 116 is D1
  • the turning radius of the turning shaft 104 when the fluid machine is operated is ⁇
  • the bearing internal clearance is ⁇ , d1, D1 , ⁇ , and ⁇ are set so as to have the relationship of Equation 1.
  • a self-lubricating cylindrical member 53 is attached to the balance bearing inner ring 52.
  • the pivot shaft end 104 b or the pivot shaft other end 104 c rotates while inscribed in the cylindrical member 53.
  • the outer diameter of the pivot shaft one end 104b or the other pivot shaft end 104c is d2
  • the inner diameter of the cylindrical member 53 is D2
  • the pivot radius of the pivot shaft 104 when the fluid machine is operated is ⁇
  • the bearing internal clearance is ⁇ .
  • d2, D2, ⁇ , and ⁇ are set so as to have the relationship of Equation 2.
  • the material of the cylindrical member 116 or 53 is generally a material called a dry bearing or a non-lubricated bearing.
  • the material include a resin whose main component is a material that is self-lubricating and excellent in slidability such as ethylene tetrafluoride, a metal coated with this resin, a resin impregnated with oil or a sintered metal, Examples thereof include a resin or metal impregnated with or coated with molybdenum sulfide.
  • the contact surface between the cylindrical member 116 and the rotation prevention pin 110 is lubricated, and wear of the rotation prevention pin 110 can be reduced.
  • the lubrication of the contact surface of the cylindrical member 53 and the other end of the turning shaft 104c is improved, and the wear of the other end of the turning shaft 104c can be reduced.
  • FIG. 27 shows a thirteenth embodiment.
  • Seal rings 48 are mounted on both sides of the orbiting scroll central portion 10d.
  • the seal ring 48 has a diameter that does not protrude from the first fixed scroll through-hole 1c and the second fixed scroll through-hole 2c even when the orbiting scroll 10 moves eccentrically.
  • the seal ring 48 slides with the bottom surfaces of the first fixed scroll 1 and the second fixed scroll 2 to seal the working chambers 21 and 22 from the outside.
  • the discharge port 108 is provided in the end plate portion of the second fixed scroll 2 and communicates with the central working chamber. Further, the orbiting end plate communication port 10 c is provided at the center of the end plate of the orbiting scroll 10.
  • the fluid sucked from the suction port 107 and compressed in the working chambers 21 and 22 is discharged from the discharge port 108 to the outside without going out from the first fixed scroll through-hole 1c and the second fixed scroll through-hole 2c.
  • the cover 117 is attached to the fixed scroll 2, no fluid flows into the cover.
  • the anti-rotation bearing (guide mechanism) 111 is not in the fluid path. Therefore, the anti-rotation bearing (guide mechanism) 111 does not reach a high temperature and is not corroded even when a corrosive fluid is handled.
  • the tip of the swivel drive shaft is displaced due to centrifugal force during high-speed rotation in the conventional structure, and the orbiting scroll wrap makes strong contact with the fixed scroll wrap, causing the wrap to wear and galling or generate noise.
  • the scroll fluid machine can be miniaturized with a high-speed rotation specification. Therefore, the present invention is highly likely to be used in vacuum pumps, fuel cell blowers, refrigerant compressors, household and packaged air conditioners, industrial air compressors, and the like that are desired to be downsized.

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 hydraulique à spirale pour l'entraînement d'une spirale rotative (10) au moyen d'un arbre rotatif (102) supporté de manière rotative sur un boîtier (100), et un arbre rotatif (104) supporté sur l'arbre rotatif (102) de manière rotative et excentrée à partir de celui-ci, une plaque anti-rotation (109) étant fixée à une extrémité de l'arbre rotatif (104) et une goupille anti-rotation (110) étant fixée sur la plaque anti-rotation (109). Un mouvement de rotation est mené avec une goupille anti-rotation (110) s'inscrivant dans un palier anti-rotation (mécanisme de guidage) (111). En variante, un mouvement de rotation est mené avec la surface périphérique externe à une extrémité (104b) de l'arbre rotatif s'inscrivant dans un palier d'équilibrage (mécanisme de guidage) (51). Avec de tels procédés, la spirale rotative qui est entraînée de manière excentrique réalise un mouvement de rotation sans provoquer de mouvement de balancement et la machine hydraulique à spirale peut fonctionner à haute vitesse.
PCT/JP2008/073096 2008-12-18 2008-12-18 Machine hydraulique à spirale WO2010070757A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN200880132361.4A CN102257276B (zh) 2008-12-18 2008-12-18 涡旋式流体机械
KR1020117015605A KR101300597B1 (ko) 2008-12-18 2008-12-18 스크롤 유체기계
PCT/JP2008/073096 WO2010070757A1 (fr) 2008-12-18 2008-12-18 Machine hydraulique à spirale
JP2010542792A JP5433831B2 (ja) 2008-12-18 2008-12-18 スクロール流体機械
US13/134,873 US20110300013A1 (en) 2008-12-18 2011-06-21 Scroll fluid machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2008/073096 WO2010070757A1 (fr) 2008-12-18 2008-12-18 Machine hydraulique à spirale

Publications (1)

Publication Number Publication Date
WO2010070757A1 true WO2010070757A1 (fr) 2010-06-24

Family

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PCT/JP2008/073096 WO2010070757A1 (fr) 2008-12-18 2008-12-18 Machine hydraulique à spirale

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US (1) US20110300013A1 (fr)
JP (1) JP5433831B2 (fr)
KR (1) KR101300597B1 (fr)
CN (1) CN102257276B (fr)
WO (1) WO2010070757A1 (fr)

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JP2012057509A (ja) * 2010-09-07 2012-03-22 Ricchisutoon:Kk スクロール流体機械
JP2021127705A (ja) * 2020-02-12 2021-09-02 有限会社スクロール技研 スクロール型真空ポンプ

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CN103291616A (zh) * 2012-03-02 2013-09-11 日本株式会社富石 涡旋式流体机械
FR3000144B1 (fr) * 2012-12-21 2018-11-16 Danfoss Commercial Compressors Compresseur a spirales ayant des premier et second joints de oldham
US8961160B2 (en) 2013-03-29 2015-02-24 Agilent Technologies, Inc. Scroll pump having separable orbiting plate scroll and method of replacing tip seal
FR3006387B1 (fr) * 2013-05-31 2016-02-19 Danfoss Commercial Compressors Compresseur a spirale
FR3011592B1 (fr) * 2013-10-08 2018-02-02 Danfoss Commercial Compressors Compresseur à spirales
JP6207970B2 (ja) * 2013-10-30 2017-10-04 サンデンホールディングス株式会社 スクロール型流体機械
CN104500395B (zh) * 2014-12-12 2016-08-17 沙无埃 涡旋压缩机
CN104612968B (zh) * 2014-12-19 2016-09-28 东北大学 一种双级涡旋干式真空泵
CN104763632B (zh) * 2015-04-08 2017-03-29 上海磁浮交通发展有限公司 一种无油涡旋空气压缩机平衡方法
CN106382220A (zh) * 2015-07-26 2017-02-08 熵零股份有限公司 涡旋流体机构
KR20170000521U (ko) 2015-07-29 2017-02-08 차진호 전면 냉각팬이 설치된 링블로어
CN107620704A (zh) * 2017-08-23 2018-01-23 南昌大学 一种机械电机一体化双侧无油涡旋压缩机
US12025126B2 (en) 2021-12-16 2024-07-02 Samsung Electronics Co., Ltd. Scroll compressor and home appliance including the same
KR20230091699A (ko) * 2021-12-16 2023-06-23 삼성전자주식회사 스크롤 압축기 및 이를 포함하는 가전기기

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JP2012057509A (ja) * 2010-09-07 2012-03-22 Ricchisutoon:Kk スクロール流体機械
JP2021127705A (ja) * 2020-02-12 2021-09-02 有限会社スクロール技研 スクロール型真空ポンプ
JP7017261B2 (ja) 2020-02-12 2022-02-08 有限会社スクロール技研 スクロール型真空ポンプ

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KR101300597B1 (ko) 2013-08-28
CN102257276B (zh) 2014-04-30
KR20120004395A (ko) 2012-01-12
CN102257276A (zh) 2011-11-23
JP5433831B2 (ja) 2014-03-05
JPWO2010070757A1 (ja) 2012-05-24
US20110300013A1 (en) 2011-12-08

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