WO2012147239A1 - スクロール型圧縮機 - Google Patents

スクロール型圧縮機 Download PDF

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Publication number
WO2012147239A1
WO2012147239A1 PCT/JP2011/080591 JP2011080591W WO2012147239A1 WO 2012147239 A1 WO2012147239 A1 WO 2012147239A1 JP 2011080591 W JP2011080591 W JP 2011080591W WO 2012147239 A1 WO2012147239 A1 WO 2012147239A1
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WO
WIPO (PCT)
Prior art keywords
scroll
fixed scroll
involute
wrap
hole
Prior art date
Application number
PCT/JP2011/080591
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
努 昆
敏 飯塚
哲広 林
克城 阿久沢
健二 相田
杉本　和禧
保則 清川
Original Assignee
三洋電機株式会社
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 三洋電機株式会社 filed Critical 三洋電機株式会社
Priority to CN201180070452.1A priority Critical patent/CN103502646B/zh
Priority to EP11864486.3A priority patent/EP2703648B1/en
Publication of WO2012147239A1 publication Critical patent/WO2012147239A1/ja

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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
    • 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
    • F04C18/0253—Details concerning the base
    • F04C18/0261—Details of the ports, e.g. location, number, 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
    • 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
    • F04C18/0269—Details concerning the involute 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
    • 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
    • F04C18/0269—Details concerning the involute wraps
    • F04C18/0284—Details of the wrap tips
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/102—Geometry of the inlet or outlet of the outlet
    • 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
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to a scroll compressor, and more particularly to a scroll compressor capable of increasing the strength on the lap center side without lowering the compression performance.
  • a scroll compressor is known as an example of a compressor that compresses refrigerant in a refrigeration cycle (see, for example, Patent Document 1).
  • the scroll compressor 100 includes a compression container 110 formed in a cylindrical shape extending in the vertical direction, and a compression element 114 that compresses a refrigerant is disposed on the upper side of the compression container 110.
  • the electric element 115 that drives the compression element 114 is disposed on the lower side.
  • the compression element 114 includes a fixed scroll 119 and an orbiting scroll 120.
  • the wraps 132 and 139 of the fixed scroll 119 and the orbiting scroll 120 are engaged with each other to form a plurality of compression spaces 121 therein. is doing.
  • the fixed scroll 119 is fixed to the casing.
  • the movable scroll 120 that meshes with the fixed scroll 119 from below is integrally connected to the drive shaft 123 by inserting the eccentric shaft portion 123A of the drive shaft 123 into the bearing portion 122 provided on the lower surface. Then, the movable scroll 120 that is rotationally driven by the driving force of the motor 127 performs only revolution without rotating with respect to the fixed scroll 119, so that the volume of the compression space 121 formed between both the laps 132 and 139 is increased. Reduce and compress the refrigerant inside.
  • the refrigerant suction pipe 117 is directly connected to the suction port 111 of the compression element 114, and the inside of the compression container 110 is filled with the high-pressure refrigerant compressed by the compression element 114.
  • a space 113 is formed.
  • the bottom of the compression container 110 serves as an oil reservoir 116 in which lubricating oil for lubricating the compression element 114 and the like is stored.
  • a side surface of the compression container 110 is provided with a refrigerant suction pipe 117 that introduces refrigerant into the compression element 114 and a refrigerant discharge pipe 118 that discharges the refrigerant compressed by the compression element 114 to the outside of the apparatus. Yes.
  • an oil passage 144 through which the lubricating oil passes is formed inside the rotating shaft 123 in order to supply the lubricating oil to the compression element 114 and the bearings 128, 141, 149, etc. of the rotating shaft 123.
  • the oil passage 144 includes a lubricating oil suction port 145 formed at the lower end of the rotation shaft 123 and a paddle 146 formed at the upper portion of the suction port 145, and is formed along the axial direction of the rotation shaft 123.
  • the oil passage 144 includes an oil supply port 147 for supplying lubricating oil at a position corresponding to each bearing.
  • the lubricating oil accumulated in the oil reservoir 116 enters the oil passage 144 from the suction port 145 of the rotating shaft 123 and is pumped upward along the paddle 146 of the oil passage 144.
  • the pumped lubricating oil lubricates the bearings 128, 141, and 149 through the oil supply ports 147.
  • the lubricating oil pumped up to the boss accommodating portion 142 is guided to the outer peripheral portion of the main frame through a return pipe (not shown) formed in the main frame, and a discharge port (not shown) formed in the outer peripheral portion. The oil is returned to the oil sump 116 again.
  • the compression part surrounded by the wrap of the fixed scroll and the wrap of the movable scroll is constituted by a space formed by these both laps meshing with each other.
  • a discharge port is formed in the central spiral portion, which is the wrap tip portion of the fixed scroll, through the thickness direction of the end plate of the fixed scroll.
  • wrapping of both a fixed scroll and a movable scroll it compresses to a high voltage
  • the present invention can increase the strength at the end plate facing the through hole near the base of the wrap tip of the fixed scroll, and thus can improve the reliability and durability.
  • a scroll compressor according to the present invention includes a fixed scroll fixed inside a casing and a movable scroll meshing with the fixed scroll, and compresses a space formed between the two wraps.
  • the wrap front end side of the fixed scroll is formed thicker than the wrap front end side of the movable scroll.
  • the inner non-involute surface which is a concave curved surface between the start point of the inner involute surface and the start point of the outer involute surface constituting the wrap of the fixed scroll.
  • non-involute surface composed of an outer non-involute surface that is a convex curved surface, and the non-involute surface is a curved surface shape having a small radius of curvature with the inner non-involute surface being a concave curved surface
  • the fixed scroll The through-hole forming the discharge port formed in the spiral center portion that is the tip of the wrap has an opening shape in the approach region facing the inner non-involute surface that is the concave curved surface, and the curvature of the inner non-involute surface that is the concave curved surface It is formed to be a curved surface smaller than the radius, It is characterized in that it is configured to ensure a long clearance distance between the closest edge that faces the base of the wrap tip of the fixed scroll in the closest state and the base part of the wrap tip of the fixed scroll.
  • the movable scroll is provided with a recess that constitutes a dummy port in an arrangement state in which at least a part of the scroll scroll is at least partially overlapped with a through hole of the fixed scroll at a spiral central portion that is a wrap tip, and the size of the recess is,
  • the through-hole of the fixed scroll and the recess of the movable scroll are formed in a positional relationship that is 180 degrees out of phase with each other.
  • the non-involute surface is formed without changing positions of both start points of the inner involute surface and the outer involute surface. It is characterized by.
  • the end plate portion facing the through hole in the vicinity of the base of the wrap tip of the fixed scroll increases the strength of the portion by the thickness.
  • the reliability and durability of the fixed scroll can be improved.
  • the scroll type compressor of the above (2) the nearest edge portion of the peripheral portion of the through hole in the fixed scroll that faces the root of the wrap tip of the fixed scroll in the closest state and the root of the wrap tip. It is possible to ensure a long distance between the adjacent holes. As a result, it is possible to further increase the strength of the end plate facing the through-hole at the root portion of the wrap tip of the fixed scroll, thereby further improving the reliability and durability of the fixed scroll. It is done.
  • the height of the vertical wall where the through hole rises from the peripheral portion facing the base of the wrap tip of the fixed scroll is increased, so that the wrap tip of the fixed scroll Since the end plate facing the through-hole at the base portion is thick, there is an advantage that the strength of the fixed scroll can be further increased accordingly.
  • the height of the vertical wall of the through hole is formed to be approximately twice the thickness of the fixed scroll lap facing the intermediate pressure chamber. The effect that the intensity
  • the scroll compressor of the above (5) there is an effect that the timing of the discharge of the refrigerant gas from the compression chamber can be achieved by providing the movable scroll with the recess that constitutes the dummy port. can get.
  • the scroll compressor of the above (6) it is possible to increase the strength of the root of the center tip without changing the design compression ratio of the spiral.
  • FIG. 1 is a longitudinal sectional view showing a scroll compressor according to an embodiment of the present invention.
  • FIG. 2 is an explanatory view showing the state of the lower surface of the fixed scroll of the scroll compressor shown in FIG.
  • FIG. 3 is a plan view showing the state of the upper surface of the movable scroll of the scroll compressor.
  • FIG. 4 is a cross-sectional view showing a state around the communication path of the scroll compressor.
  • FIG. 5A is an enlarged view of the main part showing the vicinity of the wrap tip of the fixed scroll of the scroll compressor
  • FIG. 5B is a fixed scroll (Table 1) of an ordinary general scroll compressor as a comparative example. It is a principal part enlarged view which shows the lap front-end
  • FIG. 6A is a cross-sectional view taken along line VIA-VIA in FIG. 5A
  • FIG. 6B is a cross-sectional view taken along line VIB-VIB in FIG.
  • FIG. 7 is an explanatory view showing a curved surface shape in the vicinity of the wrap tip portion in the fixed scroll of the scroll compressor shown in FIG.
  • FIG. 8 is an explanatory diagram showing the relationship between the through-holes near the wrap tip and the movable scroll dummy port in the fixed scroll shown in FIG. 7 and the relationship between the wrap thicknesses of both scrolls.
  • FIG. 9 is a cross-sectional view showing a configuration of a conventional general scroll compressor.
  • FIG. 1 shows a scroll compressor 1 having an internal high pressure according to an embodiment of the present invention, and this compressor 1 is connected to a refrigerant circuit (not shown) in which a refrigerant circulates and performs a refrigeration cycle operation.
  • the refrigerant is compressed by inverter control.
  • the compressor 1 has a vertically long cylindrical hermetic dome-shaped casing 3.
  • the casing 3 includes a casing body 5 that is a cylindrical body having an axis extending in the vertical direction, and a bowl-shaped upper cap having a convex surface that is welded and integrally joined to the upper end of the casing body 5.
  • the casing 3 accommodates a scroll compression mechanism 11 that compresses the refrigerant and a drive motor 13 that is disposed below the scroll compression mechanism 11.
  • the scroll compression mechanism 11 and the drive motor 13 are connected by a drive shaft 15 that is disposed so as to extend in the vertical direction in the casing 3.
  • a high-pressure space 17 that is a gap space is formed between the scroll compression mechanism 11 and the drive motor 13.
  • the scroll compression mechanism 11 includes a housing 21 that is a substantially bottomed cylindrical storage member that is open on the upper side, a fixed scroll 23 that is fastened with bolts in close contact with the upper surface of the housing 21, the fixed scroll 23,
  • the movable scroll 25 is disposed between the housings 21 and meshes with the fixed scroll 23.
  • the housing 21 is fixed to the casing body 5 on the outer peripheral surface thereof.
  • the casing 3 is partitioned into a high-pressure space 17 below the housing 21 and a discharge space 29 above the housing 21, and the spaces 17 and 29 are formed to extend vertically on the outer periphery of the housing 21 and the fixed scroll 23. Communicating through a vertical groove (not shown).
  • the drive motor 13 includes an annular stator 13A fixed to the inner wall surface of the casing 3, and a rotor 13B configured to be rotatable inside the stator 13A.
  • the motor 13 is composed of an inverter-controlled DC motor, and a movable scroll 25 of the scroll compression mechanism 11 is drivingly connected to the rotor 13B via a drive shaft 15.
  • the lower space 91 below the drive motor 13 is maintained at a high pressure, and oil is stored in the inner bottom portion of the lower cap 9 corresponding to the lower end portion thereof.
  • an oil supply passage 15 ⁇ / b> B as a part of the high pressure oil supply means is formed, and the oil supply passage 15 ⁇ / b> B communicates with an oil chamber 52 on the back surface of the movable scroll 25.
  • a pickup (not shown) is connected to the lower end of the drive shaft 15, and this pickup scoops up oil stored in the inner bottom portion of the lower cap 9. The scooped up oil passes through the oil supply passage 15B of the drive shaft 15 and is supplied to the oil chamber 52 on the back surface on the movable scroll 25 side. Then, the oil chamber 52 passes through a communication passage 51 and a communication hole 53 (described later) provided in the movable scroll 25 (see FIG.
  • the housing 21 is formed with a support portion 21A in which the eccentric shaft portion 15A of the drive shaft 15 rotates, and a radial bearing portion 21B extending downward from the center of the lower surface of the support portion 21A. Further, the housing 21 is provided with a radial bearing 21C penetrating between the lower end surface of the radial bearing portion 21B and the bottom surface of the support portion 21A.
  • a thin plate-like oil collector 24 that prevents the lubricating oil from entering a discharge pipe (not shown) extends along the inner peripheral surface of the casing body 5. Is suspended.
  • the upper cap 7 of the casing 3 has a suction pipe (not shown) that guides the refrigerant in the refrigerant circuit to the scroll compression mechanism 11, and the casing body 5 has a discharge pipe that discharges the refrigerant in the casing 3 to the outside of the casing 3. It is fixed in a penetrating manner.
  • the suction pipe extends vertically in the discharge space 29, and an inner end thereof passes through the fixed scroll 23 of the scroll compression mechanism 11 and communicates with the compression chamber 27, and the refrigerant is sucked into the compression chamber 27 by the suction pipe.
  • the fixed scroll 23 includes an end plate 23A, a spiral (involute) wrap 23B formed on the lower surface of the end plate 23A, and a spiral (involute) wrap 23B.
  • a through hole 23 ⁇ / b> C is formed in the central portion so as to penetrate the end plate and open toward the discharge valve 22.
  • the tip end surface lower surface 233; see FIG.
  • the movable scroll 25 includes an end plate 25A, a spiral (involute) wrap 25B formed on the upper surface of the end plate 25A, and a spiral (involute) center of the wrap 25B.
  • the recess 25 ⁇ / b> D is formed as a dummy port that adjusts the timing at which the refrigerant gas in the compression chamber 27 in a high-pressure state is discharged toward the discharge space 29.
  • the wrap 23B of the fixed scroll 23 and the wrap 25B of the movable scroll 25 are meshed with each other, and a plurality of compression chambers 27 are formed between the wraps 23B and 25B (see FIG. 1).
  • the movable scroll 25 has a flow restricting member (pin member) 55 inserted in a communication passage 51 described later.
  • the pin member 55 includes a first pin 55A that fits in the lower hole 51A on the back side of the communication path 51, and a second pin that comes into contact with the first pin 55A and fits in the insertion hole 51B on the near side of the communication path 51. It is comprised by the pin 55B.
  • a screw member with a hexagonal hole (not shown) is screwed into the female screw hole 51C so as to integrally press the second pin 55B and the first pin 55A toward the back end side, and the screw member is one end of the insertion hole 51B (FIG. 4). The left end is closed. Further, the screw member is fixed so as not to be loosened by an adhesive or the like. As shown in FIG. 1, the movable scroll 25 is supported by the fixed scroll 23 via the Oldham ring 61, and a bottomed cylindrical boss portion 25C projects from the center of the lower surface of the end plate 25A.
  • an eccentric shaft portion 15A is provided at the upper end of the drive shaft 15, and the eccentric shaft portion 15A is rotatably fitted into a boss portion 25C of the movable scroll 25.
  • the movable scroll 25 is formed with a communication passage 51 formed in the end plate 25 ⁇ / b> A with one end opened to the outside and linearly extended to the inside.
  • the communication path 51 forms a lower hole 51A of a communication path whose one end opens to the outside.
  • the lower hole 51A is reamed from one end to a predetermined depth position to form an insertion hole 51B having a predetermined depth.
  • a female screw hole 51C is screwed into the entrance of the insertion hole 51B.
  • the other end (high pressure opening) 51 ⁇ / b> D of the communication path 51 communicates with the oil chamber (high pressure portion in the hermetic container) 52 on the back surface of the movable scroll 25 described above.
  • a communication hole 53 having a perfect circle shape is opened on the inner peripheral surface on the entrance side of the communication path 51.
  • the communication hole 53 is formed in the end portion of the movable scroll 25 near the inlet facing the low pressure portion 27A of the compression chamber so as to penetrate the mirror surface 250 in the thickness direction, and is opened so that the fixed scroll 23 faces.
  • the drive shaft 15 below the radial bearing portion 21B of the housing 21 is provided with a counterweight portion 16 for dynamic balance with the movable scroll 25, the eccentric shaft portion 15A, and the like.
  • the movable scroll 25 By rotating the drive shaft 15 while balancing the weight, the movable scroll 25 is revolved without rotating. As the movable scroll 25 revolves, the compression chamber 27 is configured to compress the refrigerant sucked from the suction pipe when the volume between the wraps 23B and 25B contracts toward the center. .
  • a through hole 23 ⁇ / b> C constituting a discharge port is provided in the central portion of the fixed scroll 23, and the gas refrigerant discharged from the through hole 23 ⁇ / b> C is discharged to the discharge space 29 through the discharge valve 22. And it flows out to the space outside the oil collector 24 in the high-pressure space 17 below the housing 21 through vertical grooves (not shown) provided on the outer peripheries of the housing 21 and the fixed scroll 23.
  • Reference numerals E1 and E2 denote a major axis length in the through hole 23C of the fixed scroll 23 and a minor axis length orthogonal to the major axis length, respectively. Furthermore, the symbols e1 and e2 respectively indicate the major axis length in the recess 25D of the movable scroll 25 and the orthogonal axis length orthogonal thereto.
  • the wrap 23B is formed to have a height (h + ⁇ h) that is higher than the height (h) described in the specification 1 of Table 1 to be described later, and can be configured to increase the output as a compressor. Has been. Further, as shown in FIG.
  • the front end portion Z of the wrap 23B is the starting point P of the inner side surface (hereinafter referred to as “inner involute surface S1”) of the two surfaces constituting the wrap 23B of the fixed scroll 23.
  • a non-involute surface S3 is formed in a region ⁇ (see FIG. 5A) between the start point Q of the outer surface (hereinafter referred to as “outer involute surface S2”) of the two surfaces. .
  • the non-involute surface S3 is formed without changing the positions of both starting points of the inner involute surface S1 and the outer involute surface S2.
  • the region from point R through point Z to point Q is a convex surface portion and constitutes a convex curved surface S32 that is an outer non-involute surface of the non-involute surface S3.
  • the point Z corresponds to the vertex of the convex curved surface S32 that is the outer non-involute surface S3.
  • the point R is a starting point as a common non-involute surface for the concave curved surface S31 that is an inner non-involute surface and the convex curved surface S32 that is an outer non-involute surface.
  • the non-involute surface S3 of the present invention has a curved surface shape with a small radius of curvature r (r ⁇ r ′; r ′ represents the entire concave surface S31, particularly from the start point R to the end point P of the concave surface S31; B), the radius of curvature of the inner involute surface S′1 in the fixed scroll of the specification 1 in Table 1 described later). That is, the concave curved surface S31 has a shape as shown by a solid line shifted in a direction closer to the through hole 23C (rightward in the figure) than the inner involute surface shown by a broken line in FIG.
  • a curved surface having an appropriate shape different from the inner involute surface for example, the inner involute surface
  • An arbitrary shape such as an arc-shaped curve shifted outward may be used.
  • an arc having an appropriate curvature radius is used.
  • Desired Cartesian coordinates that is, as shown in FIG. 7, an orthogonal XY coordinate is set at a predetermined position as an origin O, and a basic circle ⁇ is drawn at the origin O on the two-dimensional coordinates.
  • the basic circle ⁇ is arbitrary for each of various compressors, and for example, the radius thereof is uniquely determined exclusively by the size of the fixed scroll and the output of the compressor.
  • intersection point P is the end point of the inner non-involute surface (ie, the concave curved surface S31) and the start point of the inner involute surface S1
  • intersection point Q is the end point of the outer non-involute surface (ie, the convex curved surface S32) and the outer involute surface S2.
  • the point R which is the starting point of the concave curved surface S31 that is the inner non-involute surface and the starting point of the convex curved surface S32 that is the outer non-involute surface, is a point where both curved surfaces intersect.
  • the non-involute surface S3 to be changed the concave curved surface S31 to be the inner non-involute surface formed in the region ⁇ 1 indicated by the two points P and R, as shown in FIG.
  • the starting point of the inner involute surface S1 is changed to the point P.
  • the installation position of the center point of the circle when forming this arc is not necessarily limited to the section PN on the straight line V, which is a tangent line, and may be on an extension line thereof.
  • the involute curve formed in the region ⁇ 1 in the region ahead of the starting point P on the already formed inner involute surface S1 is changed to an arc centered on the arbitrary point C described above.
  • the radius r of the circle in this case is smaller than the corresponding radius r ′ of the fixed roll 23 ′ of the specification 1 type (see Table 1 described later) shown in FIG. ⁇ R ′ is used.
  • the inner non-involute surface S31 formed in the region ⁇ 1 is shifted slightly outward from the inner involute curved surface before being changed to this, that is, closer to the through hole 23C.
  • the circular arc curve here, what passes through both the points of the end point P and the start point R is used.
  • the convex curved surface S32 that is the outer non-involute surface formed in the region ⁇ 2 of the three points Q, Z, and R among the region ⁇ that forms the non-involute surface S3 is described above. As you can see, it has been changed to an arc curve.
  • the through hole 23C constituting the discharge port formed in the spiral center portion of the wrap 23B of the fixed scroll 23 will be described with reference to FIGS.
  • the end plate at the point Z that is the tip of the wrap 23B of the fixed scroll 23 particularly the inner peripheral edge of the through hole 23C that forms the discharge port formed at the spiral central portion that is the tip of the wrap 23B of the fixed scroll 23.
  • close-to-hole distance L a long length (hereinafter referred to as “close-to-hole distance L”) with respect to the closest edge portion U of 23. That is, in the normal general through-hole, for example, the fixed scroll 23 'shown in FIG. 5B, the base portion with respect to the end plate 23'A at the point Z' which is the tip of the wrap 23'B (FIG. 5B ) Immediately below the portion indicated by the point Z ') and the closest edge of the fixed scroll 23' that faces the inner periphery of the through hole 23'C from the root at the tip Z 'of the wrap 23'B.
  • critical hole distance L ′ Compared to the length between U ′ (hereinafter referred to as “critical hole distance L ′”), at least the critical hole distance L of the present embodiment is longer, that is, L> L ′. It is configured as follows. As described above, the critical hole distance L in the fixed scroll 23 can be increased as compared with the critical hole distance L ′ in the fixed scroll 23 ′ of the specification 1. This is because the size is smaller than the through hole 23 ′ C in the fixed scroll 23 ′ described in 1. The base surface 232, in particular, the critical distance L, can be secured longer in the end plate 23A by the smaller amount. Therefore, in order to narrow down the through hole 23C, the present embodiment has the following configuration. In the through hole 23C of the present embodiment shown in FIG.
  • the opening area is narrowed to about 80% to 90% (in this embodiment, 90%) (see FIGS. 5A and 5B). That is, the through hole 23C has an opening shape in the approach region ( ⁇ ) facing the concave curved surface S31 of the non-involute surface S3, and the opening shape in the approach region ( ⁇ ′) in the through hole 23′C of the fixed scroll 23 ′. Compared with the opening shape, the opening is configured to be narrowed. For example, in the present embodiment, the critical hole distance L is increased by reducing the opening area by about 10%.
  • the opening radius of the through hole 23C is smaller than the radius of curvature r of the concave curved surface S31 so that the opening in the approach region ( ⁇ ) facing the concave curved surface S31 (see FIG. 5A) is narrowed. It is composed of a curved surface that forms the inner edge. That is, the opening edge in the approach region ( ⁇ ) is shifted and moved backward so as to approach toward the center direction of the through hole 23C (in FIG. 7, a portion indicated by a thick line from a portion indicated by a one-dot chain line). To the right). Thereby, the hole is narrowed to reduce the opening area.
  • the curved surface of this portion may be, for example, an arc having a radius of curvature smaller than the radius of curvature r of the concave curved surface S31.
  • region ((epsilon)) which faces the concave curved surface S31 of the non-involute surface S3 of the fixed scroll 23 approaches the hole center direction.
  • the shape of the fixed scroll 23 ′ described in the specification 1 at the through-hole 23′C is narrowed by retreating. It is the same as and has not been changed.
  • the fixed scroll according to the specification 1 of Table 1 is also used for the critical distance ⁇ L between the lap 23B and the through hole 23C at a portion slightly away from the vicinity of the tip Z of the lap 23B.
  • the size is larger than the critical hole distance ⁇ L ′ in the normal fixed scroll 23 ′ shown in FIG. 6B, which is a cross-sectional view taken along the corresponding portion 23 ′.
  • the increase of the critical hole distance ⁇ L can be realized because the through hole 23C of the fixed scroll 23 at the cut surface portion as shown in FIG.
  • the width W narrower than the width W ′ (where W ⁇ W ′) of the corresponding portion of the through hole 23′C in the fixed scroll 23 ′.
  • the through hole 23C constituting the discharge port formed in the spiral center portion that is the apex Z that is also the distal end portion of the wrap 23B of the fixed scroll 23 of the present embodiment.
  • the height H of the vertical wall 231 that rises vertically from the base surface 232, which is the surface portion connected to the base of the wrap 23B, of the mirror surface 230 of the end plate 23A of the fixed scroll 23 is increased. It has a formed configuration.
  • the wrap width t in the portion of the fixed scroll 23 excluding the lap 23B tip Z.
  • the fixed scroll 23 ′ of the specification 1 generally has a portion excluding the tip of the wrap 23′B of the fixed scroll 23 ′.
  • the vertical wall 231 ' is provided from the base surface 232' so that the height H 'is substantially the same as the width t' at H, that is, H' ⁇ t '.
  • the through-hole 23C of the present embodiment has a vertical wall 231 formed higher than a normal general through-hole, that is, the through-hole 23′C in the fixed scroll 23 ′ of the specification 1, and therefore the wrap 23B.
  • the end plate has a structure in which the thickness of the end plate 23A in the vicinity of the point Z is substantially increased, and the strength is greatly increased structurally.
  • the through hole 23C of the present embodiment is smaller than the size of the recess 25D constituting the dummy port formed in the spiral center portion of the wrap 25B of the movable scroll 25, that is, E1 ⁇ e1 and E2 ⁇ e2 It is formed to satisfy.
  • the through hole 23C is not the same area as the depression 25D, but has a smaller area.
  • the through-hole 23C of the fixed scroll 23 and the recess 25D of the movable scroll 25 are assembled in a relative positional relationship in which the phases are shifted 180 degrees from each other and reversed point-symmetrically.
  • point symmetry defines the relationship between figures that overlap each other when rotated 180 degrees around the center position of symmetry.
  • the rotor 13B rotates with respect to the stator 13A, and thereby the drive shaft 15 rotates.
  • the movable scroll 25 of the scroll compression mechanism 11 keeps its posture with respect to the fixed scroll 23 and does not rotate but only revolves.
  • the compressed refrigerant becomes high pressure and is discharged from the compression chamber 27 through the discharge valve 22 to the discharge space 29, and through the vertical grooves (not shown) provided on the outer circumferences of the housing 21 and the fixed scroll 23.
  • the high-pressure refrigerant is discharged out of the casing 3 through a discharge pipe (not shown) provided in the casing body 5.
  • the refrigerant discharged to the outside of the casing 3 circulates through a refrigerant circuit (not shown), is again sucked into the compressor 1 through the suction pipe, is compressed, and the circulation of the refrigerant is repeated.
  • a refrigerant circuit (not shown)
  • the lubricating oil stored in the inner bottom portion of the lower cap 9 in the casing 3 is scraped up by a pickup (not shown) provided at the lower end of the drive shaft 15 shown in FIG.
  • this lubricating oil is supplied to the oil supply passage 15B of the drive shaft 15. Then, the oil is supplied to the oil chamber 52 in the high pressure state on the back of the movable scroll 25. Further, the lubricating oil opens from the oil chamber 52 shown in FIG. 4 to the lower surface 233 which is the front end surface of the lap 23B on the fixed scroll 23 side through the communication passage 51 and the communication hole 53 provided in the movable scroll 25.
  • the oil groove 23 ⁇ / b> D (see FIGS. 2 and 4) is fed out using the differential pressure and supplied to the sliding portions of the scroll compression mechanism 11 and the compression chamber 27. Further, for example, in FIG.
  • the high-pressure space 17 has a thin plate shape. Since the oil collector 24, the cup 26, and the like are installed, the oil can be recovered to the inner bottom portion of the lower cap 9 while preventing entry into the discharge pipe.
  • the five types of scroll compressors provided with various types of fixed scrolls including the fixed scroll 23 according to the present embodiment are operated, the closest state to the through hole near the tip of the wrap described above
  • the specification 1 is usually a general low output type
  • the specification 2 is a general high output type.
  • the specification 5 shows the fixed scroll 23 used in the present embodiment.
  • the specification 5 corresponding to the fixed scroll of this embodiment has a scroll tooth height of ⁇ h compared to the specification 1 (low output type) which is a general configuration.
  • the discharge hole area is reduced by a factor of 0.9 and the vertical wall of the discharge hole is increased by a factor of 2.5.
  • the knowledge that the force acting on the root of the tip Z where the maximum stress of the fixed scroll was generated can be reduced by 28% by adopting such a configuration. Therefore, according to the compressor 1 of this embodiment provided with the fixed scroll shown in the specification 5, it was confirmed that the strength of the end plate 23A in the vicinity of the root Z of the wrap 23B tip Z of the fixed scroll 23 was increased.
  • this invention is not limited to the said embodiment, A various deformation
  • the fixed scroll of the present invention is not limited to the specification 5 in Table 1 above, and may have any of the specifications 3, 4 and 6.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
PCT/JP2011/080591 2011-04-28 2011-12-27 スクロール型圧縮機 WO2012147239A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201180070452.1A CN103502646B (zh) 2011-04-28 2011-12-27 涡旋型压缩机
EP11864486.3A EP2703648B1 (en) 2011-04-28 2011-12-27 Scroll compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011-101545 2011-04-28
JP2011101545A JP5879532B2 (ja) 2011-04-28 2011-04-28 スクロール型圧縮機

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CN114718863A (zh) * 2022-04-19 2022-07-08 广东美的环境科技有限公司 动涡旋盘、压缩组件和涡旋压缩机以及空调器

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US10711782B2 (en) 2017-04-20 2020-07-14 Lg Electronics Inc. Scroll compressor with wrap contour modification
KR102318124B1 (ko) * 2017-04-24 2021-10-27 엘지전자 주식회사 스크롤 압축기
FR3070446B1 (fr) 2017-08-29 2020-02-07 Danfoss Commercial Compressors Un compresseur a spirales ayant un orifice de refoulement principal central et un orifice de refoulement auxiliaire
US11078909B2 (en) * 2018-03-27 2021-08-03 Kabushiki Kaisha Toyota Jidoshokki Scroll compressor
WO2020188738A1 (ja) * 2019-03-19 2020-09-24 三菱電機株式会社 スクロール圧縮機
EP4191063A1 (en) * 2020-07-27 2023-06-07 Emerson Climate Technologies (Suzhou) Co., Ltd. Fixed scroll and scroll compressor
CN114593048A (zh) * 2022-03-15 2022-06-07 松下压缩机(大连)有限公司 一种涡旋压缩机涡旋型线结构

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EP2703648A4 (en) 2014-07-30
EP2703648A1 (en) 2014-03-05
EP2703648B1 (en) 2016-07-06
CN103502646B (zh) 2016-04-13
CN103502646A (zh) 2014-01-08
JP2012233421A (ja) 2012-11-29
JP5879532B2 (ja) 2016-03-08

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