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WO2014155646A1 - Compresseur à spirales - Google Patents

Compresseur à spirales Download PDF

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Publication number
WO2014155646A1
WO2014155646A1 PCT/JP2013/059444 JP2013059444W WO2014155646A1 WO 2014155646 A1 WO2014155646 A1 WO 2014155646A1 JP 2013059444 W JP2013059444 W JP 2013059444W WO 2014155646 A1 WO2014155646 A1 WO 2014155646A1
Authority
WO
WIPO (PCT)
Prior art keywords
tooth bottom
fixed
wrap
scroll
scroll compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2013/059444
Other languages
English (en)
Japanese (ja)
Inventor
彰士 松村
啓 武田
太田原　優
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Global Life Solutions Inc
Original Assignee
Hitachi Appliances Inc
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 Hitachi Appliances Inc filed Critical Hitachi Appliances Inc
Priority to PCT/JP2013/059444 priority Critical patent/WO2014155646A1/fr
Priority to US14/768,958 priority patent/US20160003247A1/en
Priority to JP2015507853A priority patent/JP6081577B2/ja
Priority to EP13880382.0A priority patent/EP2980408A4/fr
Priority to CN201380073432.9A priority patent/CN105074218B/zh
Publication of WO2014155646A1 publication Critical patent/WO2014155646A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—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
    • F04C18/0215—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
    • 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
    • F04C18/0276—Different wall heights
    • 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
    • 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
    • F04C29/0085—Prime movers
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/602—Gap; Clearance

Definitions

  • the present invention relates to a scroll compressor.
  • Patent Document 1 Japanese Patent No. 2009-281509
  • the spiral wrap is engaged with the fixed scroll lap to form a plurality of compression chambers.
  • an inclined surface whose thickness decreases from the outer peripheral side to the inner peripheral side is formed, thereby reducing the friction loss caused by the deformation of the fixed scroll and the orbiting scroll. It can improve the efficiency of the compressor "(see summary).
  • a lap tooth is formed on a facing surface of each of the end plates of the orbiting scroll and the fixed scroll by allowing for the deformation of the scroll and forming in advance a tooth bottom having a step difference from the outer peripheral side to the inner peripheral side. It is described that the friction loss due to the contact between the tip portion and the tooth bottom portion facing the tip portion is reduced.
  • the bottom step that is, by providing the bottom step, the contact between the lap tooth tip and the bottom portion can be suppressed, but if this bottom step is made too large, a gap is formed on the contrary, Gas leaks into the compression chamber through the gap, and the loss increases.
  • the present invention aims to suppress contact between the lap tooth tip portion and the tooth bottom portion by providing a tooth bottom step and to reduce loss due to a gap formed by increasing the tooth bottom step.
  • the present application includes a plurality of means for solving the above problems.
  • a fixed scroll having a fixed side plate portion and a fixed side wrap that is erected while maintaining a spiral shape on one surface of the fixed side plate portion;
  • Orbiting scroll that forms a compression chamber by revolving
  • An electric motor that drives the orbiting scroll via a crankshaft
  • Steps are formed in the tooth bottom portions of the fixed side wrap and the turning side wrap so as to become deeper from the outer peripheral side toward the inner peripheral side, It is characterized in that the step on the inner peripheral side in the tooth bottom part of the fixed wrap is formed deeper than the step on the inner peripheral side in the tooth bottom part of the turning side wrap ".
  • FIG. 1 is a longitudinal sectional view of a scroll compressor illustrating Example 1.
  • FIG. 3 is a top view of the tooth bottom portion of the orbiting scroll according to the first embodiment.
  • FIG. 3 is a top view of the bottom portion of the fixed scroll according to the first embodiment.
  • FIG. 6 is a diagram illustrating the first embodiment and corresponding to FIG. 5.
  • FIG. 6 is a diagram illustrating the second embodiment and corresponding to FIG. 5.
  • FIG. 7 is a diagram illustrating Example 3 and corresponding to FIG. 6.
  • FIG. 1 is an example of a configuration diagram of a scroll compressor according to the present embodiment.
  • the scroll compressor 1 includes a compression mechanism unit 2, an electric motor 3 that drives the compression mechanism unit 2, and a sealed container 4 that houses the compression mechanism unit 2, the electric motor 3, and the like.
  • This embodiment is a vertical scroll compressor in which the compression mechanism unit 2 is disposed in the upper part of the sealed container 2, the electric motor 3 is disposed in the middle part, and the oil reservoir 15 is disposed in the lower part of the sealed container 4.
  • the sealed container 4 is configured by welding a lid cap 4b and a bottom cap 4c vertically to a cylindrical chamber 4a.
  • a suction pipe 4d is disposed on the lid cap 4b, and a discharge pipe 4e is disposed on the side surface of the cylindrical chamber 4a.
  • a discharge pressure space 4 f serving as a discharge pressure is accommodated in the sealed container 4.
  • the compression mechanism 2 and the electric motor 3 are accommodated in the discharge pressure space 4f.
  • the compression mechanism unit 2 includes a fixed scroll 5, a turning scroll 6, a frame 7, and the like as basic elements. The fixed scroll 5 and the frame 7 are fastened with bolts, and the orbiting scroll 6 is supported by the frame 7.
  • FIG. 2 shows a cross-sectional view of the basic configuration of the fixed scroll 5 and the orbiting scroll 6 of the scroll compressor 1 of this embodiment.
  • the fixed scroll 5 includes a disk-shaped top plate portion (fixed side plate portion 5b), a spiral fixed side wrap 5a erected on the inner peripheral portion of the lower portion of the fixed side plate portion 5b, and a wrapping on the outer peripheral portion of the fixed side plate portion 5b.
  • a cylindrical fixed side end plate portion 5g provided so as to surround 5a, a suction port 5c and a discharge port 5d provided on the upper side of the fixed side plate portion 5b, and the like, are fixed to the frame 7 with bolts. Yes.
  • the orbiting scroll 6 includes a disk-like orbiting side plate portion 6b on the side where the fixed side wrap 5a of the fixed scroll 5 is erected, and a spiral orbiting orbiting side wrap 6a that is erected on the inner peripheral side of the orbiting side plate portion 6b. It is comprised.
  • the orbiting scroll 6 is disposed so as to be freely rotatable so that the fixed scroll 5 and the lap of each other mesh with each other and a compression chamber 16 is formed.
  • An eccentric pin portion 9b of the crankshaft 9 is connected to the back side of the orbiting scroll 6 (lower side in FIGS. 1 and 2). As the orbiting scroll 6 orbits with respect to the fixed scroll 5, a compression operation is performed in which the volume thereof is reduced.
  • Each scroll wrap (fixed side wrap 5a, turning side wrap 6a) is formed with a circular involute curve or the like as a basic curve, and is formed outside the wrap on the winding end side of the turning scroll 6 by engaging both scrolls with each other.
  • the outer-line-side compression chamber and the inner-line-side compression chamber formed on the inner side thereof are different in size and have an asymmetric scroll shape formed with a phase shifted by about 180 ° with respect to the rotation of the shaft.
  • the outer peripheral side of the frame 7 is fixed to the inner wall surface of the sealed container 4 by welding or the like, and includes a main bearing 8 that rotatably supports the crankshaft 9.
  • An Oldham ring 10 is disposed between the rear side of the orbiting scroll 6 and the frame 7.
  • the Oldham ring 10 is mounted in a groove formed on the back side of the orbiting scroll 6 and a groove formed on the frame 7 and receives the eccentric rotation of the eccentric pin portion 9b of the crankshaft 9 without the orbiting scroll 6 rotating. Arranged to revolve.
  • the electric motor 3 includes a stator 3a and a rotor 3b.
  • the stator 3a is fixed to the sealed container 4 by press-fitting, shrink fitting or the like.
  • the rotor 3b is rotatably arranged inside the stator 3a.
  • the rotor 3b is fixed to the crankshaft 9, and the orbiting scroll 6 is caused to orbit through the crankshaft 9 as the rotor 3b rotates.
  • the crankshaft 9 is composed of a main shaft 9a and an eccentric pin portion 9b, and is supported by a main bearing 8 and a sub bearing 11 provided on the frame 7.
  • the eccentric pin portion 9b is eccentrically formed integrally with the crankshaft 9a, and is inserted into the orbiting bearing 6d formed on the back surface of the orbiting scroll 6.
  • the crankshaft 9 is driven by the electric motor 3, and the eccentric pin portion 9b rotates eccentrically with respect to the main shaft 9a, thereby driving the orbiting scroll 6.
  • crankshaft 9 is provided with an oil supply passage 9c for introducing lubricating oil to the main bearing 8, the sub bearing 11, and the slewing bearing 6d, and pumps up the lubricating oil to the lower end on the oil reservoir 15 side and guides it to the oil supply passage 9c.
  • a pump unit 14 is attached.
  • the auxiliary bearing 11 is fixed to the sealed container 4 via the housing 12 and the lower frame 13.
  • the auxiliary bearing 11 rotatably holds one end of the crankshaft main shaft portion 9a on the oil reservoir side using a slide bearing, a rolling bearing, a spherical bearing member, or the like.
  • the compressed refrigerant gas is discharged from the discharge port 5d provided at the upper center of the fixed side plate portion 5b of the fixed scroll 5 to the discharge pressure space 4f in the sealed container 4 and circulates around the compression mechanism portion 2 and the electric motor 3. Then, it flows out from the discharge pipe 4e to the outside. Therefore, the space in the sealed container 4 is a so-called high pressure chamber compressor in which the discharge pressure is maintained.
  • a back pressure chamber 17 is formed between the back side of the orbiting scroll 6 and the frame 7, which is a pressure state that is intermediate between the pressure in the suction pipe 4 d and the pressure in the discharge pressure space 4 f.
  • the back pressure chamber 17 is provided in a path through which the lubricating oil passes from the oil reservoir 15 through the oil supply passage 9 c and lubricates the slewing bearing 6 d and then is supplied to the sliding portion of the compression mechanism portion 2.
  • the flat plate portion 6b of the orbiting scroll 6 is provided with a back pressure hole 6c for intermittently communicating the compression chamber 16 and the back pressure chamber 17 formed on the back of the orbiting scroll 6 so that the pressure in the back pressure chamber 17 is sucked into the suction pressure.
  • the discharge pressure is maintained at an intermediate pressure (this intermediate pressure is called back pressure).
  • the orbiting scroll 6 is pressed against the fixed scroll 5 from the back by the resultant force of the back pressure and the discharge pressure acting on the central space on the inner peripheral side of the seal member 18.
  • FIG. 3 is a diagram schematically showing the pressure deformation of the compression mechanism unit 2 of the scroll compressor.
  • the discharge pressure acts on the upper surface of the fixed scroll 5.
  • the back surface of the orbiting scroll 6 faces the back pressure chamber 17, back pressure acts on the back surface of the orbiting scroll 6 and pushes the orbiting scroll 6 upward (fixed scroll 5 side).
  • the fixed scroll 5 is deformed so as to protrude downward (orbiting scroll side) as a whole because the outer edge portion of the fixed side plate portion 5b is fixed to the sealed container 4. Since the orbiting scroll 6 is pressed against the fixed scroll 5 that is deformed downward and convex, the wrap tooth tip portion (fixed wrap tooth tip portion 5e, orbiting side wrap tooth tip portion 6e) and the lap tooth bottom portion of both scrolls are centered. The fixed side wrap tooth bottom 5f and the turning side lap tooth bottom 6f come into contact with each other. Then, each of the fixed scroll 5 and the orbiting scroll 6 is deformed so that the central portion thereof protrudes downward as a whole so as to follow the deformation of the fixed scroll 5.
  • each tooth base fixed side wrap tooth bottom part 5f, turning side wrap tooth bottom part 6f
  • the distance from the opposing tooth tip fixed side wrap tooth tip part 5e, turning side wrap tooth tip part 6e
  • I will call it the deep root difference.
  • FIG. 4 is a top view of the orbiting scroll 6 and the fixed scroll 5 of the scroll compressor 1.
  • FIG. 5 is a diagram schematically showing the relationship between the wrap tooth tip and the tooth bottom from the wrap circumferential side surface direction.
  • the level difference of the orbiting side wrap tooth bottom portion 6f of the orbiting scroll 6 is the (b) portion along the inner peripheral side with reference to the outermost tooth bottom (c) portion, and further (a ) Is set so that the depth changes in the order of parts. That is, the step is provided so that the innermost (a) portion is deepest and the outermost (c) portion is shallowest.
  • the step of the fixed side wrap tooth bottom portion 5f of the fixed scroll 5 is similar to the turning side wrap tooth bottom portion 6f of FIG.
  • the depth changes in the order of the part (b) and the part (a) along the side, and the amount of change is set equally in the orbiting scroll 6 and the fixed scroll 5. That is, the step is provided so that the innermost (a) portion is deepest and the outermost (c) portion is shallowest.
  • the steps described above are in the order of (b) part and (a) part along the inner peripheral side with reference to the outermost peripheral tooth bottom (c) part in the turning side wrap tooth bottom part 6 f.
  • the depth is set to change.
  • the part (a) is formed deeper than the part (c) so as to have a step of 0.02% to 0.04% of the turning wrap tooth height 6h
  • the part (b) is (c). 2 is formed with a depth that is a step of 0.005% to 0.02% of the turning wrap tooth height 6h
  • part (c) is the turning side with respect to the turning end plate surface 6g shown in FIG.
  • the turning side wrap tooth height 6h here shows the length from the turning side end plate surface 6g to the turning side wrap tooth tip portion 6e of the turning side wrap 6a as shown in FIG.
  • the fixed side wrap tooth bottom part 5f is also set so that the depth changes in the order of the part (b) and further the part (a) along the inner peripheral side with reference to the outermost tooth bottom (c) part.
  • the depth of the step is the same, and the part (a) is deeply formed to be a step of 0.02% to 0.04% of the fixed side wrap tooth height 5h with respect to the part (c), and the part (b) (C) is formed with a depth of 0.005% to 0.02% of the fixed-side wrap tooth height 5h with respect to the portion (c), and the portion (c) with respect to the fixed-side end plate surface 5g shown in FIG.
  • the fixed side wrap tooth height 5h indicates the length from the fixed side end plate surface 5g to the fixed side wrap tooth tip portion 5e of the fixed side wrap 5a.
  • the wrap forming surface of the orbiting side plate portion 6 b of the orbiting scroll 6 and the wrap forming surface of the fixed side plate portion 5 b of the fixed scroll 5 have a stepped side so that the step becomes deeper from the outer peripheral side toward the inner peripheral side.
  • a lap tooth bottom portion 6f and a fixed side wrap tooth bottom portion 5f are formed.
  • FIG. 6 is a view showing the depths of the turning side wrap tooth bottom portion 6f and the fixed side wrap tooth bottom portion 5f of the present embodiment.
  • the level difference of the part (a) with respect to (c) in the turning side wrap tooth bottom part 6 f and the level difference of the part (a) with respect to (c) in the fixed side wrap tooth bottom part 5 f It was formed to be 0.02% to 0.04% of each lap tooth height and was the same.
  • the step of the portion (b) with respect to (c) in the turning side wrap tooth bottom portion 6f and the step of the portion (b) with respect to (c) in the fixed side wrap tooth bottom portion 5f are 0.005% of the respective lap tooth heights. It was formed to be 0.02% and was the same.
  • the step of (a) portion with respect to (c) in the turning side wrap tooth bottom portion 6f is different from that of (a) portion with respect to (c) in the fixed side wrap tooth bottom portion 5f. It is characterized by being made smaller than the step. Specifically, the step of the portion (a) with respect to (c) in the turning side wrap tooth bottom portion 6f is formed to be 0.005% to 0.02% of the turning side wrap tooth height 6h, thereby fixing the fixed side wrap. The tooth bottom portion 5f is formed to be smaller than the step of the portion (a) with respect to (c) (0.02% to 0.04% of the fixed side wrap tooth height 5h).
  • the step amount Ds on the inner peripheral side of the orbiting side wrap tooth bottom portion 6f. ′ (Depth) is made smaller than the step amount Dk (depth) on the inner peripheral side of the fixed side lap tooth bottom part 5f, thereby filling an extra gap and improving the sealing performance. From the gap between the lap tooth tip and the tooth bottom The loss due to the leakage of the refrigerant is suppressed.
  • the refrigerant density is smaller than that of the R410A refrigerant, so that the refrigerant is likely to leak between adjacent compression chambers. It is done. Furthermore, in the case of a high-temperature refrigerant such as R32 refrigerant, the temperature during operation becomes high, and expansion of the gap between the lap tooth tip and the lap tooth bottom due to thermal expansion can be considered.
  • the present embodiment it is possible to suppress loss due to refrigerant leakage from the gap between the wrap tooth tip and the tooth bottom due to the provision of the tooth bottom step, so the R32 refrigerant can be used alone or in a refrigeration cycle.
  • a high-performance scroll compressor can be provided even when the ratio of sealing is 70% or more.
  • FIG. 7 is an example of a configuration diagram schematically showing the relationship between the wrap tooth tip and the tooth bottom from the wrap circumferential side surface direction.
  • the second embodiment is the same as the first embodiment except for the surface shape formed on the lap-facing surfaces of the orbiting scroll 6 and the fixed scroll 5, and the description of the portions having the same functions is omitted.
  • the (b) portion and (a) portion in the turning side wrap tooth bottom portion 6f have the same depth as shown in FIG.
  • the gap with the fixed side wrap tooth tip portion 5e at the deepest portion of the turning side wrap tooth bottom portion 6f on the winding start side is reduced. That is, two steps are formed on the fixed wrap tooth bottom 5f, one step is formed on the turning wrap tooth bottom 6f, and fixed by the inner circumferential side step Ds' of the turning lap tooth bottom 6f. It is characterized in that the innermost step Dk in the side wrap tooth bottom portion 5f is formed deeper.
  • the depth Ds ′ of the inner circumferential side step in the turning side wrap tooth bottom portion 6f and the depth of the second deepest step in the fixed side wrap tooth bottom portion 5f are substantially the same. It was confirmed that the loss could be reduced if.
  • the same effect as in the first embodiment can be obtained. Further, since the number of processing steps is reduced by the amount of the step difference with respect to the first embodiment, the manufacturing cost and time can be reduced. Further, the surface from (b) to (c) that faces the fixed wrap tooth tip 5e in FIG. 7 is not perpendicular to the fixed wrap tooth tip 5e as shown in FIG. The slope may be inclined in a slope shape so as to be inclined smoothly. Thereby, the leakage amount of the refrigerant
  • FIG. 8 is an example of a configuration diagram schematically showing the relationship between the wrap tooth tip and the tooth bottom from the wrap circumferential side surface direction.
  • the present embodiment is the same as the first embodiment except for the surface shape formed on the lap-facing surfaces of the orbiting scroll 6 and the fixed scroll 5, and the description of the parts having the same functions is omitted.
  • the swivel wrap tooth bottom portion 6 f of the swivel wrap tooth bottom portion 6 f is set shallow, with the bottom step height of the swivel wrap tooth bottom portion 6 f being two steps.
  • the depth of the bottom of the orbiting scroll is set to half the depth of the bottom of the fixed scroll, which reduces the amount of cutting during machining, shortens the machining time, and extends the tool life. There is an effect said.
  • the present embodiment is the same as the first to third embodiments except that the ferrite magnet motor is embedded in the rotor of the electric motor 3 of the scroll compressor, and the description of the portions having the same functions is omitted. To do.
  • the ferrite magnet motor Since ferrite magnet motors are less expensive than neodymium magnet motors, compressors that employ ferrite magnet motors can be expected to significantly reduce costs. However, the ferrite magnet motor has a problem that the efficiency particularly in the low speed region is lower than that of the neodymium magnet motor. Therefore, if the first to fourth embodiments are applied, the level difference (depth) of the bottom 6f of the orbiting scroll 6 is set smaller than the level difference (depth) of the bottom 5f of the fixed scroll 5, thereby improving the sealing performance. Since the loss due to refrigerant leakage from the gap between the lap tooth tip and the tooth bottom can be reduced, a highly efficient and low cost scroll compressor can be provided even in a low speed region.
  • the present embodiment is the same as the first to fourth embodiments except that the refrigerant used for the scroll compressor is a single R32 refrigerant, and the description of the portions having the same functions is omitted.
  • the R32 refrigerant has a global warming potential (GWP) of 675 and about 1/3 of R410A, and is a refrigerant with less environmental load.
  • GWP global warming potential
  • the density is small and the refrigerant leaks easily from the sealed space.
  • the operating temperature becomes high. There is a problem that the gap between the two becomes large.
  • the refrigerant sealed in the refrigeration cycle is set to a ratio of about 70% or more of the R32 refrigerant alone or the refrigerant sealed in the refrigeration cycle.
  • the level difference (depth) of the tooth bottom 6f of the orbiting scroll 6 is set to be smaller than the level difference (depth) of the tooth bottom 5f of the fixed scroll 5, so that an extra gap is filled and the sealing performance is improved. Since loss due to refrigerant leakage from the gap between the tooth tip and the tooth bottom can be reduced, a highly efficient scroll compressor can be provided while using a refrigerant with a small environmental load.

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

Abstract

La présente invention vise à supprimer le contact entre une partie sommet de denture à repli et une partie bas de denture grâce à l'agrandissement de la progression du bas de denture, et à limiter la perte provoquée par un interstice formé suite à l'agrandissement de la progression du bas de denture. Une spirale rotative comporte : une spirale fixe dotée d'une partie plaque plate côté spirale fixe et d'un repli côté fixe qui s'élève tout en conservant une forme de tourbillon sur une surface d'une partie plaque côté fixe ; une partie plaque côté rotatif ; et un repli côté rotatif qui s'élève tout en conservant une forme de tourbillon sur une surface de la partie plaque côté rotatif, une chambre de compression étant formée par le repli côté rotatif et le repli côté fixe qui tournent par rapport à la spirale fixe en même temps qu'ils entrent en prise. La progression du bas de denture plus proche de la périphérie interne que de la périphérie externe est conçue de manière à être plus importante dans la partie plaque côté fixe ou la partie plaque côté rotatif, et la progression du bas de denture est conçue de manière à être moins importante dans la partie plaque côté rotatif que dans la partie plaque côté fixe sur la périphérie externe ou sur la périphérie interne.
PCT/JP2013/059444 2013-03-29 2013-03-29 Compresseur à spirales Ceased WO2014155646A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
PCT/JP2013/059444 WO2014155646A1 (fr) 2013-03-29 2013-03-29 Compresseur à spirales
US14/768,958 US20160003247A1 (en) 2013-03-29 2013-03-29 Scroll Compressor
JP2015507853A JP6081577B2 (ja) 2013-03-29 2013-03-29 スクロール圧縮機
EP13880382.0A EP2980408A4 (fr) 2013-03-29 2013-03-29 Compresseur à spirales
CN201380073432.9A CN105074218B (zh) 2013-03-29 2013-03-29 涡旋压缩机

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2013/059444 WO2014155646A1 (fr) 2013-03-29 2013-03-29 Compresseur à spirales

Publications (1)

Publication Number Publication Date
WO2014155646A1 true WO2014155646A1 (fr) 2014-10-02

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WO2017130971A1 (fr) 2016-01-26 2017-08-03 ダイキン工業株式会社 Compresseur à spirales et climatiseur équipé de celui-ci
WO2018008550A1 (fr) 2016-07-06 2018-01-11 ダイキン工業株式会社 Compresseur à spirale
WO2018008495A1 (fr) * 2016-07-06 2018-01-11 ダイキン工業株式会社 Compresseur à spirale
WO2021074947A1 (fr) * 2019-10-15 2021-04-22 三菱電機株式会社 Compresseur à spirale

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CN108425845B (zh) * 2018-05-16 2024-07-09 上海加冷松芝汽车空调股份有限公司 一种涡旋压缩机
JP7304432B2 (ja) * 2019-12-24 2023-07-06 日立ジョンソンコントロールズ空調株式会社 スクロール圧縮機、及び、当該スクロール圧縮機を用いる冷凍サイクル装置

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Publication number Priority date Publication date Assignee Title
WO2017130971A1 (fr) 2016-01-26 2017-08-03 ダイキン工業株式会社 Compresseur à spirales et climatiseur équipé de celui-ci
US10502209B2 (en) 2016-01-26 2019-12-10 Daikin Industries, Ltd. Scroll compressor and air conditioning apparatus including the same
WO2018008550A1 (fr) 2016-07-06 2018-01-11 ダイキン工業株式会社 Compresseur à spirale
WO2018008495A1 (fr) * 2016-07-06 2018-01-11 ダイキン工業株式会社 Compresseur à spirale
US11047384B2 (en) 2016-07-06 2021-06-29 Daikin Industries, Ltd. Scroll compressor with non-uniform gap
WO2021074947A1 (fr) * 2019-10-15 2021-04-22 三菱電機株式会社 Compresseur à spirale
JPWO2021074947A1 (fr) * 2019-10-15 2021-04-22
JP7138807B2 (ja) 2019-10-15 2022-09-16 三菱電機株式会社 スクロール圧縮機

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CN105074218A (zh) 2015-11-18
CN105074218B (zh) 2017-10-13
JPWO2014155646A1 (ja) 2017-02-16
US20160003247A1 (en) 2016-01-07
EP2980408A1 (fr) 2016-02-03
EP2980408A4 (fr) 2016-12-21
JP6081577B2 (ja) 2017-02-15

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