WO2023149145A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
WO2023149145A1
WO2023149145A1 PCT/JP2022/048422 JP2022048422W WO2023149145A1 WO 2023149145 A1 WO2023149145 A1 WO 2023149145A1 JP 2022048422 W JP2022048422 W JP 2022048422W WO 2023149145 A1 WO2023149145 A1 WO 2023149145A1
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WO
WIPO (PCT)
Prior art keywords
back pressure
scroll
pressure chamber
orbiting scroll
drive shaft
Prior art date
Application number
PCT/JP2022/048422
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English (en)
Japanese (ja)
Inventor
昌喜 小山
遼太 飯島
康輔 貞方
Original Assignee
株式会社日立産機システム
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 株式会社日立産機システム filed Critical 株式会社日立産機システム
Publication of WO2023149145A1 publication Critical patent/WO2023149145A1/fr

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    • 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

Definitions

  • the present invention relates to a scroll compressor that compresses gas.
  • the scroll compressor includes a fixed scroll having a spiral wrap, an orbiting scroll having a spiral wrap, a drive shaft for orbiting the orbiting scroll with respect to the fixed scroll, and between the wrap of the orbiting scroll and the wrap of the fixed scroll. and a plurality of compression chambers formed by As the orbiting scroll orbits, each compression chamber compresses gas while moving along the wrap of the orbiting scroll, and finally discharges the compressed gas.
  • the pressure in multiple compression chambers becomes a thrust force acting in the direction of separating the orbiting scroll from the fixed scroll.
  • a back pressure chamber is formed on the back side of the orbiting scroll (more specifically, on the side opposite to the wrap of the orbiting scroll and in the depression of the fixed case). Introduce the gas being compressed or the discharged gas. The pressure in the back pressure chamber supports the thrust force of the orbiting scroll.
  • the thrust force of the orbiting scroll changes as the orbiting scroll orbits. More specifically, as the orbiting scroll orbits, the plurality of compression chambers move and their cross-sectional areas change, so the center of gravity of the thrust force moves. In particular, the cross-sectional areas of the plurality of compression chambers change significantly at the timing when one of the plurality of compression chambers starts discharging the compressed gas, so the position of the center of gravity of the thrust force changes significantly. At this time, the change in the moment that tends to tilt the orbiting scroll also increases, increasing the possibility that the orbiting scroll will oscillate.
  • the pressure in the back pressure chamber may become insufficient at the timing described above, causing the orbiting scroll to oscillate.
  • the discharge gas is constantly introduced into the back pressure chamber, the pressure in the back pressure chamber becomes excessive at timings other than the timing described above, and the power loss, which is the friction loss between the orbiting scroll and the fixed scroll, increases. there is a possibility.
  • the present invention has been made in view of the above matters, and one of the objects of the present invention is to suppress the oscillation of the orbiting scroll and suppress the power loss.
  • the present invention includes a plurality of means for solving the above problems.
  • the fixed scroll having a spiral wrap
  • the orbiting scroll having a spiral wrap
  • the fixed scroll a drive shaft for orbiting the orbiting scroll
  • a plurality of compression chambers formed between the wrap of the orbiting scroll and the wrap of the fixed scroll
  • a back pressure chamber formed on the back side of the orbiting scroll.
  • a communication hole formed in the orbiting scroll and communicating between the back pressure chamber and the compression chamber, wherein the back pressure chamber has a crank angle of the drive shaft within a first range.
  • it communicates with the compression chamber in the discharge process through the communication hole, and communicates with the compression chamber in the compression process through the communication hole when the crank angle of the drive shaft is in the second range.
  • swinging of the orbiting scroll can be suppressed and power loss can be suppressed.
  • FIG. 1 is an axial cross-sectional view showing the structure of an orbiting scroll in a first embodiment to which the present invention is applied;
  • FIG. 3 is a plan view according to arrow III in FIG. 2;
  • FIG. 3 is a radial cross-sectional view taken along line IV-IV of FIG. 2;
  • FIG. 4 is a diagram showing changes in pressure in compression chambers and opening sections of communication holes in the first embodiment to which the present invention is applied.
  • FIG. 2 is a radial cross-sectional view taken along line VII-VII in FIG. 1, showing the structure of the back pressure chamber in the first embodiment to which the present invention is applied;
  • FIG. 4 is a diagram showing movement of the center of the orbiting scroll and movement of the center of gravity of the thrust force in the first embodiment to which the present invention is applied;
  • FIG. 5 is a radial cross-sectional view showing the structure of a back pressure chamber in a second embodiment to which the present invention is applied;
  • FIG. 10 is a plan view showing the structure of an orbiting scroll in a second embodiment to which the present invention is applied;
  • FIG. 6 is a radial cross-sectional view showing the structure of an orbiting scroll in a second embodiment to which the present invention is applied; It is a figure showing the opening section of a communicating hole while showing the change of the pressure of the compression chamber in 2nd Embodiment to which this invention is applied.
  • FIG. 11 is a radial cross-sectional view showing the structure of a back pressure chamber in a third embodiment to which the present invention is applied;
  • FIG. 1 is an axial cross-sectional view showing the structure of the scroll compressor in this embodiment.
  • FIG. 2 is an axial sectional view showing the structure of the orbiting scroll in this embodiment.
  • 3 is a plan view along arrow III in FIG. 2
  • FIG. 4 is a radial sectional view along arrow IV-IV in FIG. 5(a) and 5(b) are diagrams showing the compression chamber in this embodiment.
  • FIG. 6 is a diagram showing changes in the pressure of the compression chambers in the present embodiment, as well as opening sections of the communication holes.
  • FIG. 7 is a radial cross-sectional view taken along line VII-VII in FIG. 1, showing the structure of the back pressure chamber in this embodiment. Note that FIG. 1 shows the center O1 of the drive shaft and the center O2 of the crank portion of the drive shaft. 5A, 5B, and 7 show an XY coordinate system with the center O1 of the drive shaft as the origin.
  • the scroll compressor of this embodiment includes a casing 10, a fixed scroll 11, an orbiting scroll 12, and a drive shaft 13.
  • the fixed scroll 11 is connected to the opening side of the casing 10 (left side in FIG. 1).
  • the orbiting scroll 12 is housed inside the casing 10 and faces the fixed scroll 11 .
  • the drive shaft 13 is rotatably supported by bearings 14 inside the casing 10 .
  • the fixed scroll 11 includes a substantially circular end plate 15, a spiral wrap 16 standing on one side of the end plate 15 (on the right side in FIG. 1), and a spiral wrap 16 standing on the opposite side of the end plate 15 (on the left side in FIG. 1). and a plurality of radiation fins 17 provided.
  • a suction channel for sucking gas such as air is formed in the radially outer portion of the end plate 15 .
  • a discharge passage for discharging the compressed gas is formed in the radial center of the end plate 15, and a discharge pipe 18 is connected to this discharge passage.
  • the orbiting scroll 12 includes a substantially circular end plate 19, a spiral wrap 20 erected on one surface side (left side in FIG. 1) of the end plate 19, and an opposite surface side (right side in FIG. 1) of the end plate 19. and a plate 22 provided on the tip side of the plurality of heat radiation fins 21 (on the right side in FIG. 1).
  • the winding angle of the wrap 20 of the orbiting scroll 12 is different from the winding angle of the wrap 16 of the fixed scroll 11 (asymmetric wrap structure). This makes it possible to increase the compression volume or reduce the size of the machine compared to the case where the winding angle of the wrap 20 of the orbiting scroll 12 is the same as the winding angle of the wrap 16 of the fixed scroll 11 (symmetrical wrap structure). be.
  • a crank portion 23 is provided on one end side of the drive shaft 13 (left side in FIG. 1).
  • the center O2 of the crank portion 23 of the drive shaft 13 is eccentric from the center O1 of the drive shaft 13 and is connected to the boss portion of the plate 22 of the orbiting scroll 12 via the orbiting bearing 24 .
  • the crank angle of the drive shaft 13 is the rotation angle of the straight line connecting the centers O1 and O2 described above, and is based on the angle (0°) at which the outer peripheral side compression chamber described later starts compressing gas. Note that the center O ⁇ b>2 of the crank portion 23 of the drive shaft 13 corresponds to the center of the orbiting scroll 12 .
  • the other end side (right side in FIG. 1) of the drive shaft 13 protrudes outside the casing 10 and is provided with a pulley 25 .
  • a belt (not shown) is stretched between a pulley (not shown) provided on a rotary shaft (not shown) of the electric motor and the pulley 25 .
  • the rotational force of the electric motor is transmitted, the drive shaft 13 rotates, and the orbiting scroll 12 orbits with respect to the fixed scroll 11 .
  • a rotation prevention mechanism 26 for preventing rotation of the orbiting scroll 12 is provided in the casing 10 .
  • the anti-rotation mechanism 26 includes three auxiliary crankshafts that are spaced apart from each other in the circumferential direction of the drive shaft 13, and a plate 22 of the orbiting scroll 12 that supports one end sides of the three auxiliary crankshafts. and three bearings that are provided in the casing 10 and support the other end sides of the three auxiliary crankshafts, respectively.
  • a plurality of compression chambers are formed between the wraps 20 of the orbiting scroll 12 and the wraps 16 of the fixed scroll 11.
  • the plurality of compression chambers include a plurality of outer peripheral side compression chambers 27A formed between the outer peripheral side of the wrap 20 of the orbiting scroll 12 and the inner peripheral side of the wrap 16 of the fixed scroll 11, and the inner peripheral side of the wrap 20 of the orbiting scroll 12. and a plurality of inner peripheral side compression chambers 27B formed between the outer peripheral side of the wrap 16 of the fixed scroll 11 (see FIGS. 5(a) and 5(b)).
  • the outer compression chamber 27A moves along the wrap 20 of the orbiting scroll 12, compresses the gas (compression process), and finally discharges the compressed gas through the discharge pipe 18.
  • gas compression is started when the crank angle of the drive shaft 13 is 0°. Then, as the crank angle of the drive shaft 13 increases, the gas is compressed while moving along the wrap 20 of the orbiting scroll 12, so the pressure increases (see FIG. 6). Then, when the crank angle of the drive shaft 13 reaches 1310° (in other words, when the drive shaft 13 rotates three times and the crank angle of the drive shaft 13 reaches 230°), the discharge of the compressed gas is started. . During discharge of the compressed gas, the discharge pressure (maximum pressure) is reached.
  • the inner peripheral compression chamber 27B compresses the gas (compression process) while moving along the wrap 20 of the orbiting scroll 12, and finally discharges the compressed gas through the discharge pipe 18.
  • discharge process gas compression is started when the crank angle of the drive shaft 13 is 180°. Then, as the crank angle of the drive shaft 13 increases, the gas is compressed while moving along the wrap 20 of the orbiting scroll 12, so the pressure increases (see FIG. 6). Then, when the crank angle of the drive shaft 13 reaches 1370° (in other words, when the drive shaft 13 rotates three times and the crank angle of the drive shaft 13 reaches 290°), discharge of the compressed gas is started. . During discharge of the compressed gas, the discharge pressure (maximum pressure) is reached.
  • the pressure in the plurality of compression chambers becomes a thrust force acting in the direction (rightward direction in FIG. 1) separating the orbiting scroll 12 from the fixed scroll 11.
  • the back pressure chamber 28 is formed on the back side of the orbiting scroll 12 (in other words, the side of the orbiting scroll 12 opposite to the wrap 20), and the back pressure chamber 28 and the outer compression chamber 27A are separated.
  • a communicating hole 29 is formed in the orbiting scroll 12 (specifically, the end plate 19, the radiation fins 21, and the plate 22), and the compressed gas is introduced from the outer peripheral side compression chamber 27A to the back pressure chamber 28 through the communicating hole 29. .
  • the pressure of the back pressure chamber 28 and the bearing of the anti-rotation mechanism 26 support the thrust force of the orbiting scroll 12 .
  • the back pressure chamber 28 of the present embodiment is formed by a depression in the support plate 30 fixed inside the casing 10 and is formed in an annular shape extending all the way around the drive shaft 13 in the circumferential direction.
  • a seal ring 31 is attached to the inner peripheral side and the outer peripheral side of the back pressure chamber 28 to suppress leakage of compressed gas from the back pressure chamber 28 .
  • FIG. 8 is a diagram showing the movement (trajectory) of the center of the orbiting scroll 12 and the movement (change in position) of the center of gravity of the thrust force.
  • the thrust force of the orbiting scroll 12 changes. More specifically, as the orbiting scroll 12 orbits, the plurality of compression chambers move and their cross-sectional areas change, so the center of gravity of the thrust force moves. In particular, when the crank angle of the drive shaft 13 reaches the first crank angle (230° in this embodiment) at which the outer compression chamber 27A starts discharging the compressed gas, the cross-sectional areas of the plurality of compression chambers change significantly. Therefore, the position of the center of gravity of the thrust force changes greatly.
  • crank angle of the drive shaft 13 reaches the second crank angle (290° in this embodiment) at which the inner compression chamber 27B starts discharging the compressed gas
  • the cross-sectional areas of the plurality of compression chambers are large. Since it changes, the position of the center of gravity of the thrust force changes greatly. Therefore, the change in the moment that tends to tilt the orbiting scroll 12 also increases, increasing the possibility that the orbiting scroll 12 swings.
  • the crank angle of the drive shaft 13 is in a first range including the above-described first crank angle and second crank angle (a range of 230° or more and 300° or less in this embodiment). , it communicates with the outer peripheral side compression chamber 27A in the discharge process (corresponding range of 1310° or more and 1380° or less as shown in FIG. 6) through the communication hole 29 . At this time, the pressure in the back pressure chamber 28 becomes the discharge pressure (maximum pressure). Therefore, swinging of the orbiting scroll 12 can be suppressed. As a result, leakage of compressed gas from the compression chamber can be suppressed.
  • the back pressure chamber 28 of the present embodiment has a crank angle of the drive shaft 13 in a second range (20° or more and less than 230° in this embodiment) that does not include the first crank angle and the second crank angle. At some point, it communicates with the outer peripheral side compression chamber 27A in the compression process (corresponding range of 1100° or more and less than 1310° as shown in FIG. 6) through the communication hole 29 . At this time, the pressure in the back pressure chamber 28 increases as the crank angle of the drive shaft 13 increases, but is lower than the discharge pressure. Therefore, the force that presses the orbiting scroll 12 against the fixed scroll 11 can be suppressed, and the power loss, which is the frictional loss between the orbiting scroll 12 and the fixed scroll 11, can be suppressed.
  • FIG. 9 A second embodiment to which the present invention is applied will be described with reference to FIGS. 9 to 12.
  • FIG. 9 the same code
  • FIG. 9 is a radial cross-sectional view showing the structure of the back pressure chamber in this embodiment, and corresponds to FIG. 7 described above.
  • FIG. 10 is a plan view showing the structure of the orbiting scroll in this embodiment, and corresponds to FIG. 3 described above.
  • FIG. 11 is a radial cross-sectional view showing the structure of the orbiting scroll in this embodiment, and corresponds to FIG. 4 described above.
  • FIG. 12 is a diagram showing changes in the pressure of the compression chambers and opening sections of the communication holes in this embodiment, and corresponds to FIG. 6 described above.
  • the back pressure chamber 28A of this embodiment corresponds to the third range of the crank angle of the drive shaft 13 (in this embodiment, the range of 230° to 350°) including the above-described first crank angle and second crank angle. It is formed in a part of the drive shaft 13 in the circumferential direction.
  • a seal ring 31 is attached to the outer peripheral side of the back pressure chamber 28A to suppress leakage of compressed gas from the back pressure chamber 28A.
  • the back pressure chamber 28A of the present embodiment communicates with the outer compression chamber 27A in the discharge process through the communication hole 29 when the crank angle of the drive shaft 13 is in the first range.
  • the crank angle of the drive shaft 13 is in the second range, it communicates with the outer peripheral side compression chamber 27A in the compression process via the communication hole 29 .
  • the scroll compressor of this embodiment includes other back pressure chambers 32A and 32B formed on the back side of the orbiting scroll 12, and another back pressure chamber 32A formed in the orbiting scroll 12 and inner peripheral side compression in the compression process.
  • Another communication hole 33A that communicates with the chamber 27B, and another communication hole 33B that is formed in the orbiting scroll 12 and communicates with the other back pressure chamber 32B and the outer peripheral side compression chamber 27A in the compression process.
  • the other back pressure chambers 32A, 32B are formed by depressions of the support plate 30, like the back pressure chamber 28A.
  • the other back pressure chambers 32A and 32B are formed in other ranges in the circumferential direction of the drive shaft 13 different from the back pressure chamber 28A.
  • a seal ring 31 is attached to the outer peripheral side of the other back pressure chambers 32A, 32B to suppress leakage of compressed gas from the other back pressure chambers 32A, 32B.
  • the other back pressure chamber 32A is compressed through another communication hole 33A when the crank angle of the drive shaft 13 is within a predetermined range (40° to 360° in this embodiment). , communicates with the corresponding inner peripheral side compression chamber 27B in the range of 580° to 900°.
  • the pressure in the other back pressure chamber 32A increases as the crank angle of the drive shaft 13 increases, but is lower than the pressure in the back pressure chamber 28A.
  • the other back pressure chamber 32B is compressed through another communication hole 33B when the crank angle of the drive shaft 13 is within a predetermined range (ranges of 120° to 360° and 0° to 50° in this embodiment). It communicates with the outer peripheral side compression chamber 27A in the process (corresponding range of 660° to 950° as shown in FIG. 12). The pressure in the other back pressure chamber 32B increases as the crank angle of the drive shaft 13 increases, but is lower than the pressure in the back pressure chamber 28A.
  • the back pressure chamber 28B of the present embodiment corresponds to the third crank angle range (220° to 300° range in the present embodiment) of the drive shaft 13 including the first crank angle and the second crank angle described above. It is formed in a part of the drive shaft 13 in the circumferential direction.
  • a seal ring 31 is attached to the outer peripheral side of the back pressure chamber 28B to suppress leakage of compressed gas from the back pressure chamber 28B.
  • the back pressure chamber 28B of the present embodiment is configured such that when the crank angle of the drive shaft 13 is within the first range, the pressure of the back pressure chamber 28B is increased through the communication hole 29 during the discharge process. 27A, and when the crank angle of the drive shaft 13 is in the second range, it communicates with the outer peripheral side compression chamber 27A in the compression process via the communication hole 29.
  • the scroll compressor of this embodiment includes another back pressure chamber 32C formed on the back side of the orbiting scroll 12, another back pressure chamber 32C formed in the orbiting scroll 12, and an inner peripheral side compression chamber 27B in the compression process.
  • another communication hole for example, the other communication hole 33A or 33B described above
  • communicates with the outer peripheral side compression chamber 27A in the compression process is provided.
  • the other back pressure chamber 32C is formed by a recess in the support plate 30, like the back pressure chamber 28B.
  • the other back pressure chamber 32C is formed so as to surround the back pressure chamber 28B and extend all around the drive shaft 13 in the circumferential direction.
  • a seal ring 31 is attached to the outer peripheral side of the other back pressure chamber 32C to suppress leakage of compressed gas from the other back pressure chamber 32C.
  • the other back pressure chamber 32C communicates with the inner compression chamber 27B in the compression process or the outer compression chamber 27A in the compression process through another communication hole when the crank angle of the drive shaft 13 is within a predetermined range. .
  • the pressure in the other back pressure chamber 32C increases as the crank angle of the drive shaft 13 increases, but is lower than the pressure in the back pressure chamber 28B.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne un compresseur à spirale dans lequel le balancement d'une spirale orbitale peut être supprimé et la perte de puissance peut être supprimée.　Le compresseur à spirale comprend une spirale fixe 11 présentant une enveloppe en spirale 16, une spirale orbitale 12 présentant une enveloppe en spirale 20, un arbre d'entraînement 13 qui amène la spirale orbitale 12 à tourner par rapport à la spirale fixe 11, une pluralité de chambres de compression formées entre l'enveloppe 20 de la spirale orbitale 12 et l'enveloppe 16 de la spirale fixe 11, une chambre de contre-pression 28 formée sur le côté de surface arrière de la spirale orbitale 12, et un trou de communication 29 formé dans la spirale orbitale 12 de sorte que la chambre de contre-pression 28 et la chambre de compression communiquent l'une avec l'autre à travers celles-ci. La chambre de contre-pression 28 communique avec la chambre de compression pendant un processus de décharge par l'intermédiaire du trou de communication 29 lorsque l'angle de vilebrequin de l'arbre d'entraînement 13 se trouve dans une première plage et communique avec la chambre de compression pendant un processus de compression par l'intermédiaire du trou de communication 29 lorsque l'angle de vilebrequin de l'arbre d'entraînement 13 se trouve dans une seconde plage.
PCT/JP2022/048422 2022-02-03 2022-12-27 Compresseur à spirale WO2023149145A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2022-015340 2022-02-03
JP2022015340A JP2023113179A (ja) 2022-02-03 2022-02-03 スクロール圧縮機

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Publication Number Publication Date
WO2023149145A1 true WO2023149145A1 (fr) 2023-08-10

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PCT/JP2022/048422 WO2023149145A1 (fr) 2022-02-03 2022-12-27 Compresseur à spirale

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JP (1) JP2023113179A (fr)
WO (1) WO2023149145A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63106388A (ja) * 1986-10-23 1988-05-11 Daikin Ind Ltd スクロ−ル流体装置
JPH08121366A (ja) * 1994-10-24 1996-05-14 Hitachi Ltd スクロール圧縮機
JP2011052603A (ja) * 2009-09-02 2011-03-17 Daikin Industries Ltd スクロール圧縮機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63106388A (ja) * 1986-10-23 1988-05-11 Daikin Ind Ltd スクロ−ル流体装置
JPH08121366A (ja) * 1994-10-24 1996-05-14 Hitachi Ltd スクロール圧縮機
JP2011052603A (ja) * 2009-09-02 2011-03-17 Daikin Industries Ltd スクロール圧縮機

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JP2023113179A (ja) 2023-08-16

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