US20240011488A1 - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
US20240011488A1
US20240011488A1 US18/251,994 US202118251994A US2024011488A1 US 20240011488 A1 US20240011488 A1 US 20240011488A1 US 202118251994 A US202118251994 A US 202118251994A US 2024011488 A1 US2024011488 A1 US 2024011488A1
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United States
Prior art keywords
movable
wrap
compression chamber
fixed
scroll
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Pending
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US18/251,994
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English (en)
Inventor
Atsuo Teshima
Taizo Sato
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Sanden Corp
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Sanden Corp
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Assigned to SANDEN CORPORATION reassignment SANDEN CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SATO, TAIZO, Teshima, Atsuo
Publication of US20240011488A1 publication Critical patent/US20240011488A1/en
Pending legal-status Critical Current

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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
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • F01C17/063—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with only rolling 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
    • 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
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • 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

Definitions

  • the present invention relates to a scroll compressor.
  • the scroll compressor disclosed in Patent Document 1 includes a scroll unit including a fixed scroll and a movable scroll, and an anti-rotation mechanism that prevents the rotation of the movable scroll.
  • the fixed and movable scrolls are configured such that a spiral wrap is erected on a bottom plate, and the center of the base plate and the center (spiral center) of the base circle of the wrap are shifted from each other; and a closed space is formed in the scroll unit by meshing the fixed scroll with the movable scroll such that the wraps of the fixed and movable scrolls face each other.
  • the volume of the closed space is changed by revolving the movable scroll around the axial center of the fixed scroll while preventing the rotation of the movable scroll with the anti-rotation mechanism.
  • Patent Document 1 discloses that the anti-rotation mechanism is implemented by a circular hole formed on the back surface of the bottom plate of the movable scroll and a pin that protrudes from a housing wall facing the back surface of the bottom plate of the movable scroll and engages with the circular hole. Also, according to Patent Document 1, a rotational moment occurs in the movable scroll because of a compression reaction force resulting from the compression of the scroll compressor, and a load caused by the rotational moment is applied to the anti-rotation mechanism.
  • the inventors of the present invention have discovered a phenomenon that during the operation of the scroll compressor as described above, the rotational moment momentarily disappears, and as a result, the pin momentarily moves away from the inner surface of the circular hole and then collides again with the inner surface of the circular hole.
  • An object of the present invention is to suppress reduced rotational moments that occur at the movable scroll.
  • a scroll compressor includes a fixed scroll including a fixed bottom plate having a discharge hole in the center of the fixed bottom plate, and a spiral fixed wrap erected on the fixed bottom plate, a movable scroll including a movable bottom plate and a spiral movable wrap that is erected on the movable bottom plate and is meshed with the fixed wrap, a first compression chamber formed by an inner wall surface of the movable wrap and an outer wall surface of the fixed wrap, a second compression chamber formed by an inner wall surface of the fixed wrap and an outer wall surface of the movable wrap, and an anti-rotation mechanism that prevents the rotation of the movable scroll.
  • the scroll compressor is configured such that the movable scroll is caused to revolve around the axial center of the fixed scroll while the rotation of the movable scroll is prevented by the anti-rotation mechanism to change the volume of the first compression chamber and the volume of the second compression chamber and thereby cause a fluid in the first compression chamber and a fluid in the second compression chamber to be compressed separately and then discharged together through the discharge hole into a discharge chamber.
  • an involute angle from a reference point on a base circle of the fixed wrap to a winding terminal end of the fixed wrap is less than an involute angle from a reference point on a base circle of the movable wrap to a winding terminal end of the movable wrap.
  • a winding terminal end of the movable wrap contacts the outer wall surface of the fixed wrap and the first compression chamber is thereby closed
  • a winding terminal end of the fixed wrap contacts the outer wall surface of the movable wrap and the second compression chamber is thereby closed.
  • the pressure in the first compression chamber becomes constantly higher than the pressure in the second compression chamber. This makes it possible to constantly generate a rotational moment in the movable scroll and thereby makes it possible to suppress reduced rotational moments.
  • FIG. 1 is a cross-sectional view of a scroll compressor according to an embodiment of the present invention
  • FIG. 2 is a plan view of a fixed scroll
  • FIG. 3 is a plan view of a movable scroll
  • FIG. 4 is a cross-sectional view taken along line A-A of FIG. 3 ;
  • FIG. 5 is an enlarged cross-sectional view of one of rotation prevention parts constituting an anti-rotation mechanism
  • FIG. 6 is a drawing illustrating a layout of rotation prevention parts of an anti-rotation mechanism on a movable bottom plate
  • FIG. 7 is a drawing illustrating an operating state of the scroll compressor
  • FIG. 8 is a drawing illustrating an operating state of the scroll compressor
  • FIG. 9 is a drawing illustrating an operating state of the scroll compressor
  • FIG. 10 is a drawing illustrating an operating state of the scroll compressor
  • FIG. 11 is a drawing illustrating an operating state of the scroll compressor
  • FIG. 12 is a graph showing relationships between pressures in compression chambers and a crank angle.
  • FIG. 13 is a graph showing a relationship between a force (rotational moment) applied to a pin and a crank angle.
  • FIGS. 1 to 6 illustrate a configuration of a scroll compressor according to an embodiment of the present invention.
  • FIG. 1 is a cross-sectional view illustrating an overall configuration of the scroll compressor.
  • FIG. 2 is a plan view of a fixed scroll.
  • FIG. 3 is a plan view of a movable scroll.
  • FIG. 4 is a cross-sectional view taken along line A-A of FIG. 3 .
  • FIG. 5 is an enlarged cross-sectional view of one of rotation prevention parts constituting an anti-rotation mechanism.
  • FIG. 6 is a drawing illustrating a layout of the rotation prevention parts of the anti-rotation mechanism on a movable bottom plate.
  • a scroll compressor 1 includes a scroll unit 4 including a fixed scroll 2 and a movable scroll (orbiting scroll) 3 that are disposed to face each other in a central axis direction.
  • the fixed scroll 2 includes a spiral fixed wrap 2 b that is integrally erected on a fixed bottom plate 2 a .
  • the movable scroll 3 includes a spiral movable wrap (orbiting wrap) 3 b that is integrally erected on a movable bottom plate (orbiting bottom plate) 3 a.
  • the fixed wrap 2 b and the movable wrap 3 b are formed, respectively, along involute curves (virtual lines) that extend from base circles (virtual circles) 2 c and 3 c .
  • an involute angle ⁇ 1 illustrated in FIG. 2 indicates an angle that is around a center (fixed spiral center) 2 d of the base circle 2 c and from a reference point (the start point of the involute curve) 2 e on the base circle 2 c to a winding terminal end 2 f of the fixed wrap 2 b .
  • 3 is an angle that is around a center (movable spiral center) 3 d of the base circle 3 c and from a reference point (the start point of the involute curve) 3 e on the base circle 3 c to a winding terminal end 3 f of the movable wrap 3 b.
  • the involute angle ⁇ 1 is less than the involute angle ⁇ 2 .
  • the involute angle ⁇ 1 is 820 degrees, and the involute angle ⁇ 2 is 850 degrees.
  • the involute angles ⁇ 1 and ⁇ 2 are not limited to these values. Increasing the difference between the involute angle ⁇ 2 and the involute angle ⁇ 1 increases the pressure difference between a first compression chamber C 1 and a second compression chamber C 2 described later and makes it possible to increase the rotational moment that occurs at the movable scroll 3 .
  • the fixed wrap 2 b is formed such that the center 2 d of the base circle 2 c is shifted from the center (not shown) of the fixed bottom plate 2 a .
  • the movable wrap 3 b is formed such that the center 3 d of the base circle 3 c is shifted from the center (not shown) of the movable bottom plate 3 a .
  • the fixed scroll 2 and the movable scroll 3 are disposed such that the fixed wrap 2 b is meshed with the movable wrap 3 b , a protruding end of the fixed wrap 2 b contacts the movable bottom plate 3 a , and a protruding end of the movable wrap 3 b contacts the fixed bottom plate 2 a .
  • a chip seal is provided on each of the projecting end of the fixed wrap 2 b and the projecting end of the movable wrap 3 b.
  • the fixed scroll 2 and the movable scroll 3 are disposed such that the wall surface of the fixed wrap 2 b and the wall surface of the movable wrap 3 b partially contact each other in a state in which the angles in the circumferential direction of the fixed wrap 2 b and the movable wrap 3 b are shifted from each other.
  • a crescent-shaped first compression chamber C 1 is formed by an inner wall surface 3 b 1 of the movable wrap 3 b and an outer wall surface 2 b 2 of the fixed wrap 2 b
  • a crescent-shaped second compression chamber C 2 is formed by an inner wall surface 2 b 1 of the fixed wrap 2 b and an outer wall surface 3 b 2 of the movable wrap 3 b (see FIGS. 7 and 8 , described later).
  • the movable scroll 3 is attached such that the center (axial center) of the movable bottom plate 3 a is shifted from the center (axial center) of the fixed bottom plate 2 a and is caused by a drive mechanism to revolve around the center of the fixed bottom plate 2 a while being prevented from rotating by an anti-rotation mechanism 30 , described later.
  • the radius of the revolution may be determined by a contact between the fixed wrap 2 b and the movable wrap 3 b .
  • the first compression chamber C 1 and the second compression chamber C 2 move from the winding terminal end 3 f of the movable wrap 3 b and the winding terminal end 2 f of the fixed wrap 2 b toward the center, and the volume of the first compression chamber C 1 and the volume of the second compression chamber C 2 decrease. Accordingly, a fluid (for example, a refrigerant gas) taken into the first compression chamber C 1 from the winding terminal end 3 f of the movable wrap 3 b is compressed, and a fluid (for example, a refrigerant gas) taken into the second compression chamber C 2 from the winding terminal end 2 f of the fixed wrap 2 b is compressed.
  • a fluid for example, a refrigerant gas
  • a recess 3 h is formed at a winding start end 3 g of the movable wrap 3 b .
  • the recess 3 h is indented from the inner wall surface 3 b 1 of the winding start end 3 g of the movable wrap 3 b.
  • a housing of the scroll compressor 1 includes a center housing 6 that houses the scroll unit 4 , a front housing 7 disposed in front of the center housing 6 , and a rear housing 8 disposed behind the center housing 6 .
  • the center housing 6 is formed as a housing (outer shell) for the scroll unit 4 and is integrally formed together with the fixed scroll 2 .
  • the fixed scroll 2 and the center housing 6 may be provided as separate components, and the fixed scroll 2 may be housed in and fixed to the center housing 6 .
  • the rear side of the center housing 6 is closed by the fixed bottom plate 2 a , and the front side of the center housing 6 is open.
  • the front housing 7 is fastened to the opening side of the center housing 6 with bolts (not shown).
  • the front housing 7 supports the movable scroll 3 in a thrust direction and also houses a drive mechanism for the movable scroll 3 .
  • an intake chamber 9 for the fluid is formed inside of the front housing 7 .
  • the intake chamber 9 is connected to an intake port (not shown) formed in the outer wall of the front housing 7 .
  • a bulging part 10 is formed in parts in the circumferential direction of the front housing 7 and the center housing 6 .
  • a fluid passage space 11 is formed inside of the bulging part 10 , extends in a direction parallel to the compressor central axis, and guides the fluid from the intake chamber 9 in the front housing 7 to the vicinity of the winding terminal end 2 f of the fixed wrap 2 b of the scroll unit 4 in the center housing 6 and to the vicinity of the winding terminal end 3 f of the movable wrap 3 b.
  • the rear housing 8 is fastened, with bolts 12 , to an end of the center housing 6 to face the fixed bottom plate 2 a such that a discharge chamber 13 for the fluid is formed between the rear housing 8 and the back surface of the fixed bottom plate 2 a .
  • a discharge hole 14 for discharging a compressed fluid is formed in the center of the fixed bottom plate 2 a and a discharge valve 15 , which is, for example, a one-way valve, is provided for the discharge hole 14 .
  • the discharge hole 14 is connected to the discharge chamber 13 via the discharge valve 15 .
  • the discharge chamber 13 is connected to a discharge port (not shown) that is formed in the outer wall of the rear housing 8 .
  • the fluid is introduced from the intake port into the intake chamber 9 in the front housing 7 , is taken into the first compression chamber C 1 and the second compression chamber C 2 from the outer periphery of the scroll unit 4 via the fluid passage space 11 inside of the bulging part 10 of the front housing 7 and the center housing 6 , and is then compressed.
  • the fluid compressed in the first compression chamber C 1 and the fluid compressed in the second compression chamber C 2 are combined and discharged from the discharge hole 14 , which is formed in the center of the fixed bottom plate 2 a , into the discharge chamber 13 in the rear housing 8 , and are discharged to the outside via the discharge port.
  • the front housing 7 includes a thrust receiver 17 that is disposed inside of an outer peripheral part fastened with bolts (not shown) to the opening side of the center housing 6 and faces the back surface of the movable bottom plate 3 a .
  • the thrust receiver 17 receives a thrust force from the movable scroll 3 via a thrust plate 16 .
  • a central part of the front housing 7 rotatably supports a drive shaft 20 that constitutes the core of the drive mechanism for the movable scroll 3 .
  • One end of the drive shaft 20 protrudes from the front housing 7 , and a pulley 22 is attached to the one end of the drive shaft 20 via an electromagnetic clutch 21 .
  • the drive shaft 20 is rotated by a rotational driving force that is input from the pulley 22 via the electromagnetic clutch 21 .
  • Another end of the drive shaft 20 is connected to the movable scroll 3 via a crank mechanism.
  • the crank mechanism includes a cylindrical boss 23 protruding from the back surface of the movable bottom plate 3 a and an eccentric bushing 25 eccentrically attached to a crank 24 provided at an end of the drive shaft 20 .
  • the eccentric bushing 25 is fit into the boss 23 via a bearing (e.g., a sliding bearing) 26 .
  • a balance weight 27 is attached to the eccentric bushing 25 to counterbalance the centrifugal force generated when the movable scroll 3 is driven.
  • the anti-rotation mechanism 30 is constituted by multiple (five, in the present embodiment) rotation prevention parts 33 that are arranged at regular intervals along the circumferential direction near the outer edge of the back surface of the movable bottom plate 3 a .
  • each of the rotation prevention parts 33 includes a ring 31 press-fit into a circular hole formed in the back surface (which faces the thrust receiver 17 of the front housing 7 ) of the movable bottom plate 3 a and a pin 32 that protrudes from the thrust receiver 17 of the front housing 7 , passes through the thrust plate 16 , and is loosely fit in the inside of the ring 31 .
  • at least three rotation prevention parts 33 are necessary to prevent the movable scroll 3 from rotating, while enabling the movable scroll 3 to revolve around the axial center of the fixed scroll 2 .
  • FIGS. 7 through 11 illustrate operating states of the scroll compressor 1 .
  • FIG. 12 is a graph showing the relationships between the pressures in the first compression chamber C 1 , the second compression chamber C 2 , and a final compression chamber C 4 and a crank angle.
  • FIG. 13 is a graph showing a relationship between a force (rotational moment) applied to the pin 32 and a crank angle.
  • a solid curve in FIG. 13 corresponds to the scroll compressor 1 of the present embodiment
  • a dashed curve in FIG. 13 corresponds to a related-art scroll compressor.
  • the involute angle ⁇ 1 is the same as the involute angle ⁇ 2 , and the size (at least the length in a direction along the involute curve of the movable wrap 3 b ) of the recess 3 h is smaller than the size of the recess 3 h in the present embodiment.
  • the drive shaft 20 is rotated by the electromagnetic clutch 21 , and the movable scroll 3 is caused by the crank mechanism to revolve around the axial center of the fixed scroll 2 while being prevented from rotating by the anti-rotation mechanism 30 .
  • the fluid refrigerant gas
  • the fluid is taken into the first compression chamber C 1 and the second compression chamber C 2 between the fixed wrap 2 b and the movable wrap 3 b of the scroll unit 4 from the intake port and via the intake chamber 9 and the fluid passage space 11 .
  • the involute angle ⁇ 1 ending at the winding terminal end 2 f of the fixed wrap 2 b is less than the involute angle ⁇ 2 ending at the winding terminal end 3 f of the movable wrap 3 b . Accordingly, after the winding terminal end 3 f of the movable wrap 3 b contacts the outer wall surface 2 b 2 of the fixed wrap 2 b and the first compression chamber C 1 is thereby closed, as illustrated in FIG. 7 , the winding terminal end 2 f of the fixed wrap 2 b contacts the outer wall surface 3 b 2 of the movable wrap 3 b and the second compression chamber C 2 is thereby closed, as illustrated in FIG. 8 .
  • the first compression chamber C 1 always compresses the fluid ahead of the second compression chamber C 2 , the pressure in the first compression chamber C 1 is always higher than the pressure in the second compression chamber C 2 (see crank angles of 0 to 360 degrees in FIG. 12 ).
  • the rotational moment generated in the scroll compressor 1 becomes always greater than the rotational moment generated in the related-art scroll compressor (see FIG. 13 ).
  • the direction of the rotational moment corresponds to the direction of the revolution of the movable scroll 3 .
  • the fluid compressed as a result of the reduction in the volume of the first compression chamber C 1 caused by the revolution of the movable scroll 3 combines with the fluid in a third compression chamber C 3 located in the center through the recess 3 h of the movable wrap 3 b . That is, in or after the operating state illustrated in FIG. 9 , the first compression chamber C 1 communicates with the third compression chamber C 3 through the recess 3 h of the movable wrap 3 b .
  • the third compression chamber C 3 includes the discharge hole 14 and is surrounded by the fixed wrap 2 b and the movable wrap 3 b .
  • the discharge valve 15 is closed, and the pressure in the third compression chamber C 3 is higher than the pressure in the first compression chamber C 1 . Accordingly, in a period in which the operating state illustrated in FIG. 9 changes to the operating state illustrated in FIG. 10 , the high-pressure fluid in the third compression chamber C 3 flows into (flows back into) the first compression chamber C 1 through the recess 3 h of the movable wrap 3 b . As a result, the pressure in the first compression chamber C 1 sharply increases (see crank angle ⁇ in FIGS. 12 and 13 ). In the present embodiment, the crank angle ⁇ is, for example, 310 degrees, but it is not limited thereto.
  • this configuration makes it possible to suppress reduced rotational moments at crank angles from a to 360 degrees compared to the related-art scroll compressor.
  • the fluid compressed as a result of the reduction in the volume of the second compression chamber C 2 caused by the revolution of the movable scroll 3 combines with the fluid in the first compression chamber C 1 that has been combined with the fluid in the third compression chamber C 3 . That is, immediately after the operating state illustrated in FIG. 10 , the first compression chamber C 1 , the second compression chamber C 2 , and the third compression chamber C 3 are combined to form the final compression chamber C 4 , and as a result, the second compression chamber C 2 communicates with the discharge hole 14 .
  • FIG. 12 shows that the fluid in the final compression chamber C 4 is compressed and the pressure in the final compression chamber C 4 increases at or after the crank angle of 360 degrees.
  • the discharge valve 15 opens, and the fluid in the final compression chamber C 4 is discharged through the discharge hole 14 into the discharge chamber 13 .
  • the center of the movable bottom plate 3 a is shifted from the center 3 d of the base circle 3 c of the movable wrap 3 b .
  • a distance L (not shown) between the center of the compression reaction force applied to the movable scroll 3 and the center of the movable bottom plate 3 a varies during one revolution of the movable scroll 3 .
  • the center of the compression reaction force applied to the movable scroll 3 is at the midpoint between the center 2 d of the base circle 2 c and the center 3 d of the base circle 3 c when the pressure in the first compression chamber C 1 is the same as the pressure in the second compression chamber C 2 .
  • the center of the compression reaction force moves further away from the center of the movable bottom plate 3 a (in other words, the distance L increases); and in the opposite case, the center of the compression reaction force moves closer to the center of the movable bottom plate 3 a (in other words, the distance L decreases).
  • the distance L is smallest at around each of the crank angles of 0, 360, and 720 degrees shown in FIGS. 12 and 13 .
  • the rotational moment described above indicates a moment around the center of the movable bottom plate 3 a and is the product of the compression reaction force and the distance L.
  • the compression reaction force varies during one revolution of the movable scroll 3 and is smallest at around, for example, each of the crank angles of 0, 360, and 720 degrees shown in FIGS. 12 and 13 .
  • the crank angle at which the distance L is smallest is close to the crank angle at which the compression reaction force is smallest, there is a concern that the rotational moment at that angle (at around a crank angle of 0, 360, or 720 degrees) may be reduced.
  • the involute angle ⁇ 1 ending at the winding terminal end 2 f of the fixed wrap 2 b is made less than the involute angle ⁇ 2 ending at the winding terminal end 3 f of the movable wrap 3 b .
  • the first compression chamber C 1 always compresses the fluid ahead of the second compression chamber C 2 , the pressure in the first compression chamber C 1 is always higher than the pressure in the second compression chamber C 2 (see crank angles of 0 to 360 degrees in FIG. 12 ). This makes it possible to raise the level of the rotational moment to be generated (see FIG. 13 ).
  • the second compression chamber C 2 communicates with the discharge hole 14 .
  • this makes it possible to increase the difference between the pressure in the first compression chamber C 1 and the pressure in the second compression chamber C 2 at crank angles between a and 360 degrees as shown in FIGS. 12 and 13 (see FIG. 12 ) and thereby makes it possible to suppress reduced rotational moments (see FIG. 13 ).
  • Adopting the measures [1] and [2] described above makes it possible to suppress reduced rotational moments and thereby makes it possible to cause the pin 32 to be always in contact with the inner surface of the ring 31 . This in turn makes it possible to prevent the pin 32 from colliding with the ring 31 and thereby makes it possible to reduce the occurrence of vibration and noise in the anti-rotation mechanism 30 .
  • the scroll compressor 1 includes the fixed scroll 2 including the fixed bottom plate 2 a having the discharge hole 14 in the center of the fixed bottom plate 2 a and the spiral fixed wrap 2 b erected on the fixed bottom plate 2 a , the movable scroll 3 including the movable bottom plate 3 a and the spiral movable wrap 3 b that is erected on the movable bottom plate 3 a and is meshed with the fixed wrap 2 b , the first compression chamber C 1 formed by the inner wall surface 3 b 1 of the movable wrap 3 b and the outer wall surface 2 b 2 of the fixed wrap 2 b , the second compression chamber C 2 formed by the inner wall surface 2 b 1 of the fixed wrap 2 b and the outer wall surface 3 b 2 of the movable wrap 3 b , and the anti-rotation mechanism 30 that prevents the rotation of the movable scroll 3 .
  • the scroll compressor 1 is configured such that the movable scroll 3 is caused to revolve around the axial center of the fixed scroll 2 while the rotation of the movable scroll 3 is prevented by the anti-rotation mechanism 30 to change the volume of the first compression chamber C 1 and the volume of the second compression chamber C 2 and thereby cause the fluid in the first compression chamber C 1 and the fluid in the second compression chamber C 2 to be compressed separately and then discharged together through the discharge hole 14 into the discharge chamber 13 .
  • the fixed wrap 2 b may be formed according to an involute curve that is based on the base circle 2 c of the fixed wrap 2 b .
  • the movable wrap 3 b may be formed according to an involute curve that is based on the base circle 3 c of the movable wrap 3 b .
  • the involute angle ⁇ 1 from the reference point 2 e on the base circle 2 c of the fixed wrap 2 b to the winding terminal end 2 f of the fixed wrap 2 b is less than the involute angle ⁇ 2 from the reference point 3 e on the base circle 3 c of the movable wrap 3 b to the winding terminal end 3 f of the movable wrap 3 b .
  • the movable wrap 3 b includes the recess 3 h that is formed at the winding start end 3 g of the movable wrap 3 b and is indented from the inner wall surface 3 b 1 of the winding start end 3 g .
  • the scroll compressor 1 further includes the third compression chamber C 3 that includes the discharge hole 14 and is surrounded by the fixed wrap 2 b and the movable wrap 3 b .
  • the second compression chamber C 2 communicates with the discharge hole 14 . This makes it possible to increase the difference between the pressure in the first compression chamber C 1 and the pressure in the second compression chamber C 2 and thereby makes it possible to suppress reduced rotational moments.
  • the anti-rotation mechanism 30 includes the ring 31 that is press-fit into the circular hole formed in one of the back surface of the movable bottom plate 3 a and the housing wall facing the back surface and the pin 32 that protrudes from another one of the back surface and the housing wall and is loosely fit in the inside of the ring 31 .
  • the anti-rotation mechanism 30 it possible to reduce the occurrence of vibration and noise in the anti-rotation mechanism 30 .
  • the center of the fixed bottom plate 2 a is shifted from the center 2 d of the base circle 2 c of the fixed wrap 2 b .
  • the center of the movable bottom plate 3 a is shifted from the center 3 d of the base circle 3 c of the movable wrap 3 b .
  • An external drive source for driving the scroll compressor 1 of the present embodiment may be, for example, a vehicle engine or a motor.
  • the scroll compressor 1 may include, as an integral component, a motor that serves as the drive source.
  • the scroll compressor 1 of the present embodiment may be incorporated into a refrigerant circuit of a vehicle air conditioner and configured to compress and discharge a refrigerant that is taken in from the low pressure side of the refrigerant circuit.
  • the scroll unit 4 (the fixed scroll 2 and the movable scroll 3 ) described above may also be used for a scroll expander.
  • the scroll expander may be incorporated into a refrigerant circuit of a Rankine cycle device for a vehicle and configured to expand a refrigerant introduced from the refrigerant circuit to generate power (or recover power from the refrigerant).
  • outer wall surface 3 c . . . base circle, 3 d . . . center, 3 e . . . reference point, 3 f . . . winding terminal end, 3 g . . . winding start end, 3 h . . . recess, 4 . . . scroll unit, 6 . . . center housing, 7 . . . front housing, 8 . . . rear housing, 9 . . . intake chamber, 10 . . . bulging part, 11 . . . fluid passage space, 13 . . . discharge chamber, 14 . . . discharge hole, 15 . . . discharge valve, 20 . . .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US18/251,994 2020-11-24 2021-10-15 Scroll compressor Pending US20240011488A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2020-194330 2020-11-24
JP2020194330A JP2022083079A (ja) 2020-11-24 2020-11-24 スクロール圧縮機
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JP3350039B2 (ja) * 2002-02-06 2002-11-25 三菱重工業株式会社 スクロール型流体機械
JP6207942B2 (ja) 2013-09-19 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
JP6460710B2 (ja) * 2014-10-03 2019-01-30 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
JP2017053279A (ja) * 2015-09-10 2017-03-16 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド スクロール圧縮機

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