US20160003247A1 - Scroll Compressor - Google Patents

Scroll Compressor Download PDF

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Publication number
US20160003247A1
US20160003247A1 US14/768,958 US201314768958A US2016003247A1 US 20160003247 A1 US20160003247 A1 US 20160003247A1 US 201314768958 A US201314768958 A US 201314768958A US 2016003247 A1 US2016003247 A1 US 2016003247A1
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US
United States
Prior art keywords
orbiting
fixed
tooth bottom
side wrap
scroll
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.)
Abandoned
Application number
US14/768,958
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English (en)
Inventor
Shoji Matsumura
Hiromu Takeda
Masaru Ohtahara
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Hitachi Johnson Controls Air Conditioning Inc
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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
Assigned to HITACHI APPLIANCES, INC. reassignment HITACHI APPLIANCES, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MATSUMURA, SHOJI, OHTAHARA, MASARU, TAKEDA, HIROMU
Publication of US20160003247A1 publication Critical patent/US20160003247A1/en
Assigned to JOHNSON CONTROLS-HITACHI AIR CONDITIONING TECHNOLOGY (HONG KONG) LIMITED reassignment JOHNSON CONTROLS-HITACHI AIR CONDITIONING TECHNOLOGY (HONG KONG) LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HITACHI APPLIANCES, INC.
Assigned to HITACHI-JOHNSON CONTROLS AIR CONDITIONING, INC. reassignment HITACHI-JOHNSON CONTROLS AIR CONDITIONING, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JOHNSON CONTROLS-HITACHI AIR CONDITIONING TECHNOLOGY (HONG KONG) LIMITED
Abandoned 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 Literature 1 Japanese Patent No. 2009-281509 (Patent Literature 1) as background art of the subject technical field discloses that “There is an inclined surface having the plate thickness reduced from the outer peripheral side to the inner peripheral side preliminarily formed on the surface of the mirror plate of the orbiting scroll, which faces the mirror plate of the fixed scroll in expectation of the scroll deformation.
  • the fixed scroll has a spiral wrap standing on the inner periphery of the flat plate, and a cylindrical mirror plate mounted on the outer periphery to surround the wrap.
  • the orbiting scroll has a standing spiral wrap in mesh with the fixed scroll wrap on the mirror plate opposite the fixed scroll at the side of the standing wrap to form a plurality of compression chambers.” This makes it possible to “improve efficiency of the compressor by reducing the friction loss caused by deformations of the fixed scroll and the orbiting scroll” (see abstract).
  • Patent Literature 1 discloses that the tooth bottoms are preliminarily formed on opposite surfaces of mirror plates of the orbiting scroll and the fixed scroll, each step of which has the depth increased from the outer peripheral side to the inner peripheral side in expectation of the scroll deformation, reducing the friction loss caused by the contact between the wrap tooth tip and the opposing tooth bottom.
  • the thus formed tooth bottom step may suppress the contact between the wrap tooth tip and the tooth bottom. If the tooth bottom step is unnecessarily widened, the gap is generated, through which gas leaks to the inside of the compression chamber, thus increasing the loss.
  • the present invention includes a plurality of means for solving the problem, one of which will be described as an example below.
  • the present invention provides a scroll compressor which includes a fixed scroll including a fixed-side plate and a fixed-side wrap standing on one surface of the fixed-side plate while retaining a spiral shape, an orbiting scroll including an orbiting-side plate, and an orbiting-side wrap standing on one surface of the orbiting-side plate while retaining a spiral shape, which allows the orbiting-side wrap to be in mesh with the fixed-side wrap for orbiting with respect to the fixed scroll to form a compression chamber, and an electric motor for driving the orbiting scroll via a crankshaft.
  • Each tooth bottom of the fixed-side wrap and the orbiting-side wrap has a step formed to become deeper from an outer periphery to an inner periphery. The step is formed on the tooth bottom of the fixed-side wrap at the inner periphery so as to be deeper than the step formed on the tooth bottom of the orbiting-side wrap at the inner periphery.
  • the present invention is capable of suppressing the contact between the wrap tooth tip and the tooth bottom by forming the tooth bottom step, and reducing the loss caused by the gap generated as a result of enlarging the tooth bottom step.
  • FIG. 1 is a longitudinal sectional view of a first embodiment of a scroll compressor.
  • FIG. 2 is a view showing structures of the fixed scroll and the orbiting scroll.
  • FIG. 3 is a schematic view representing pressure deformation of the rear part of the scroll compressor according to the first embodiment.
  • FIG. 4 ( 1 ) is a top view of the tooth bottom of the orbiting scroll according to the first embodiment.
  • FIG. 4 ( 2 ) is a top view of the tooth bottom of the fixed scroll according to the first embodiment.
  • FIG. 5 is an explanatory view showing each wrap structure of the orbiting scroll and the fixed scroll.
  • FIG. 6 is a view showing the first embodiment corresponding to FIG. 5 .
  • FIG. 7 is a view showing a second embodiment corresponding to FIG. 5 .
  • FIG. 8 is a view showing a third embodiment corresponding to FIG. 6 .
  • scroll compressor which is configured to optimize the gap between wraps so as to suppress the load exerted to the wrap and to reduce the loss caused by leakage into the compression chamber.
  • FIG. 1 shows an example of the structure of the scroll compressor according to the embodiment.
  • a scroll compressor 1 includes a compression mechanism part 2 , an electric motor 3 for driving the compression mechanism part 2 , and a closed vessel 4 for storing the compression mechanism part 2 and the electric motor 3 .
  • the embodiment is formed as a vertical scroll compressor configured to have the compression mechanism part 2 disposed at the upper section in the closed vessel 2 , the electric motor 3 disposed in the intermediate section, and an oil sump 15 disposed at the lower section of the closed vessel 4 .
  • the closed vessel 4 is formed by welding a lid cap 4 b and a bottom cap 4 c to top and bottom parts of a cylindrical chamber 4 a.
  • An intake pipe 4 d is mounted to the lid cap 4 b, and a discharge pipe 4 e is mounted to the side surface of the cylindrical chamber 4 a.
  • the closed vessel 4 has discharge pressure space 4 f working as the discharge pressure therein.
  • the compression mechanism part 2 and the electric motor 3 are stored in the discharge pressure space 4 f.
  • the compression mechanism part 2 includes a fixed scroll 5 , an orbiting scroll 6 , and a frame 7 as basic components.
  • the fixed scroll 5 and the frame 7 are secured with a bolt, and the orbiting scroll 6 is supported with the frame 7 .
  • FIG. 2 shows cross-sections of basic structures of the fixed scroll 5 and the orbiting scroll 6 of the scroll compressor 1 according to the embodiment.
  • the fixed scroll 5 includes a disc-like top plate (fixed-side plate 5 b ), a spiral fixed-side wrap 5 a which stands on the inner periphery at the lower section of the fixed-side plate 5 b, a cylindrical fixed-side mirror plate 5 g disposed on the outer periphery of the fixed-side plate 5 b to surround the wrap 5 a, and an intake port 5 c and a discharge port 5 d which are provided at the upper section of the fixed-side plate 5 b.
  • the fixed scroll as described above is secured to the frame 7 with the bolt.
  • the orbiting scroll 6 includes a disc-like orbiting-side plate 6 b, and a spiral orbiting-side wrap 6 a, standing on the inner periphery of the orbiting-side plate 6 b at the side where the fixed-side wrap 5 a of the fixed scroll 5 stands.
  • the orbiting scroll 6 is orbitally arranged so as to allow the wrap to be in mesh with the wrap of the fixed scroll 5 to form compression chambers 16 .
  • An eccentric pin 9 b of a crankshaft 9 is connected to a back surface side of the orbiting scroll 6 (the lower side as shown in FIGS. 1 and 2 ). The orbiting motion of the orbiting scroll 6 with respect to the fixed scroll 5 ensures compression to reduce the volume thereof.
  • Each scroll wrap (fixed-side wrap 5 a, orbiting-side wrap 6 a ) is formed of an involute curve of the circle as the basic curve, and has an asymmetrical scroll shape, having a compression chamber at the outer line side formed outside the wrap at a winding end side of the orbiting scroll 6 and a compression chamber at the inner line side formed inside the wrap each having the different size in the state where both scrolls are meshed with each other, and each phase is shifted at approximately 180° with respect to rotation of the shaft.
  • the outer periphery of the frame 7 is secured to an inner wall surface of the closed vessel 4 through welding, and provided with a main bearing 8 which supports the crankshaft 9 rotatably.
  • An Oldham ring 10 is disposed between the back surface side of the orbiting scroll 6 and the frame 7
  • the Oldham ring 10 is fitted in the grooves formed in the back surface side of the orbiting scroll 6 and in the frame 7 so that the orbiting scroll 6 revolves in association with eccentric rotation of the eccentric pin 9 b of the crankshaft 9 while being kept from rotating.
  • the electric motor 3 includes a stator 3 a and a rotor 3 b.
  • the stator 3 a is secured to the closed vessel through press fitting, shrink fitting and the like.
  • the rotor 3 b is rotatably disposed at the inner side of the stator 3 a.
  • the rotor 3 b is secured to the crankshaft 9 , through which the orbiting scroll 6 is oar operated by rotation of the rotor 3 b.
  • the crankshaft 9 includes a main shaft 9 a and an eccentric pin 9 b, which is supported with a main bearing 8 and a sub bearing 11 .
  • the eccentric pin 9 b is integrally formed with the crankshaft 9 a with eccentricity therebetween, and is inserted into an orbiting bearing 6 d formed on the back surface of the orbiting scroll 6 .
  • the crankshaft 9 is driven by the electric motor 3 , and the eccentric pin 9 b eccentrically rotates with respect to the main shaft 9 a so that the orbiting scroll 6 is driven.
  • the crankshaft 9 includes an oil passage 9 c formed therein for guiding the lubricant to the main bearing 8 , the sub bearing 11 and the orbiting bearing 6 d.
  • a pump 14 is disposed at the lower end of the oil sump 15 for drawing the lubricant so as to be guided into the oil passage 9 c.
  • the sub bearing 11 is secured to the closed vessel 4 via a housing 12 and a lower frame 13 .
  • the sub bearing 11 rotatably retains one end of the main shaft 9 a of the crankshaft at the side of the oil sump using a slide bearing, a roll bearing, a spherical bearing member and the like.
  • the work fluid such as refrigerant gas is introduced from the intake pipe 4 d into the compression chambers 16 defined by the orbiting scroll 6 and the fixed scroll 5 .
  • the refrigerant gas has its volume reduced toward the center of the scroll for compression.
  • the compressed refrigerant gas is discharged from the discharge port 5 d formed in the upper center of the fixed-side plate 5 b of the fixed scroll 5 into the discharge pressure space 4 f in the closed vessel 4 .
  • the gas then circulates around the compression mechanism part 2 and the electric motor 3 , and flows to the outside from the discharge pipe 4 e.
  • the space within the closed vessel 4 serves as so called high pressure chamber compressor where the discharge pressure is held.
  • a back pressure chamber 17 is formed between the back surface side of the orbiting scroll 6 and the frame 7 , where the pressure is kept to the intermediate level between the pressure inside the intake pipe 4 d and the pressure in the discharge pressure space 4 f.
  • the back pressure chamber 17 is disposed on the path through which the lubricant is fed to the sliding part of the compression mechanism part 2 after passing through the oil passage 9 c from the oil sump 15 for lubricating the orbiting bearing 6 d.
  • the flat plate 6 b of the orbiting scroll 6 has a back pressure hole 6 c for intermittently communicating the compression chamber 16 and the back pressure chamber 17 formed on the hack surface of the orbiting scroll so that the pressure in the back pressure chamber 17 is kept to the intermediate level (hereinafter referred to as the back pressure) between the intake pressure and the discharge pressure.
  • the resultant force of the back pressure and the discharge pressure applied to the space at the center on the inner peripheral side of a seal member 18 allows the orbiting scroll 6 to be pressed against the fixed scroll 5 from the back surface.
  • FIG. 3 schematically shows the pressure deformation of the compression mechanism part 2 of the scroll compressor.
  • the section above the fixed scroll 5 faces the discharge pressure space 4 f so that the discharge pressure is applied to the upper surface of the fixed scroll 5 .
  • the back surface of the orbiting scroll 6 faces the back pressure chamber 17 , the back pressure is applied to the back surface of the orbiting scroll 6 which is pushed upward (side of the fixed scroll 5 ).
  • the scroll compressor shown in FIG. 3 is configured that the fixed scroll 5 has the outer edge of the fixed-side plate 5 b secured to the closed vessel 4 , it will be deformed into the convex shape directed downward as a whole (orbiting scroll side).
  • the respective wrap tooth tips fixed-side wrap tooth tip 5 e, orbiting-side wrap tooth tip 6 e
  • the respective wrap tooth tips fixed-side wrap tooth tip 5 e, orbiting-side wrap tooth tip 6 e
  • the respective wrap tooth tips fixed-side wrap tooth tip 5 e, orbiting-side wrap tooth tip 6 e
  • the respective wrap tooth bottoms fixed-side wrap tooth bottom 5 f, orbiting-side wrap tooth bottom 6 f
  • Each of the fixed scroll 5 and the orbiting scroll 6 has the center part downwardly deformed into the convex shape as a whole along the deformation of the fixed scroll 5 .
  • the maximum displacement at the wrap center becomes further large, which makes each contact of the center between the fixed-side wrap tooth tip 5 e and the orbiting-side wrap tooth bottom 6 f, and between the fixed-side wrap tooth bottom 5 f and the orbiting-side tooth tip 6 e excessively strong.
  • the tooth bottom step which becomes deeper from the outer side to the center is formed on each tooth bottom of the orbiting scroll 6 and the fixed scroll 5 (fixed-side wrap tooth bottom 5 f, orbiting-side wrap tooth bottom 6 f ), respectively. It is assumed that the tooth bottom step becomes deeper as the distance increases between the tooth bottom (fixed-side wrap tooth bottom 5 f, orbiting-side wrap booth bottom 6 f ) and the opposite tooth tip (fixed-side wrap tooth tip 5 e, orbiting-side wrap tooth tip 6 e ).
  • FIG. 4 shows the orbiting scroll 6 and the fixed scroll 5 of the scroll compressor 1 as top views.
  • FIG. 5 schematically represents the relationship between the wrap tooth tip and the tooth bottom seen from the direction of the wrap circumferential side.
  • the step of the orbiting-side wrap tooth bottom 6 f of the orbiting scroll 6 is set to change its depth from the part (c) as the reference depth at the outermost periphery to the part (b) along the inner periphery, and further to the part (a) sequentially.
  • the step is formed so that the part (a) at the innermost periphery becomes the deepest, and the part (c) at the outermost periphery becomes the shallowest.
  • the step of the fixed-side wrap tooth bottom 5 f of the fixed scroll 5 is set to change its depth from the part (c) as the reference depth to the part (b) along the inner periphery, and further to the part (a) sequentially.
  • the steps of the orbiting scroll 6 and the fixed scroll 5 are set to have each depth equally changed. In other words, the step is formed so that the part (a) at the innermost periphery is the deepest, and the part (c) at the outermost periphery is the shallowest.
  • the above-described step on the orbiting-side wrap tooth bottom 6 f is set so that the depth is changed from the part (c) as the reference at the outermost periphery to the part (b) along the inner periphery, and further to the part (a) sequentially.
  • the part (a) is formed to have the depth different from the part (c) by approximately 0.02% to 0.04% of the orbiting-side wrap tooth height 6 h
  • the part (b) is formed to have the depth different from the part (c) by approximately 0.005% to 0.02% of the orbiting-side wrap tooth height 6 h
  • the part (c) is formed to have the depth of approximately 0.00% to 0.03% of the orbiting-side wrap tooth height 6 h with respect to the orbiting-side mirror plate surface 6 g shown in FIG. 2
  • the orbiting-side wrap tooth height 6 h denotes the length from the orbiting-side mirror plate surface 6 g to the orbiting-side wrap tooth tip 6 e of the orbiting-side wrap 6 a as shown in FIG. 2 .
  • the step on the fixed-side wrap tooth bottom 5 f is set so that the depth is changed from the part (c) as the reference at the outermost periphery to the part (b) along the inner periphery, and further to the part (a) sequentially.
  • the part (a) is formed to have the depth different from the part (c) by 0.02% to 0.04% of the fixed-side wrap.
  • the fixed-side wrap tooth height 5 h in this case denotes the length from the fixed-side mirror plate surface 5 g to the fixed-side wrap tooth tip 5 e of the fixed-side wrap 5 a.
  • the structure shown in FIGS. 4 and 5 serves Lo prevent excessive contact between the fixed-side wrap tooth bottom 5 f and the orbiting-side wrap tooth tip 6 e, or between the orbiting-side wrap tooth bottom 6 f and the fixed-side wrap tooth tip 5 e, and to ensure suppression of increase in the input by friction and improvement of reliability with respect to the wrap strength.
  • the scroll compressor with the structure shown in FIGS. 4 and 5 is configured that each difference in the tooth bottom steps formed on the fixed-side wrap tooth bottom 5 f and the orbiting-side wrap tooth bottom 6 f is equally set, resulting in unnecessary gap under the condition of maximum wrap deformation. Examinations made by the inventors have revealed the problem that under the operating condition (condition of low-speed and low-pressure ratio) of small wrap deformation, the step formed on the tooth bottom will further generate the gap, through which the refrigerant leaks between the compression chambers, resulting in the loss.
  • FIGS. 4 and 6 hereinafter as an embodiment for preventing increase in the loss caused by leakage of the refrigerant through the gap between the wrap tooth tip and the wrap tooth bottom.
  • the orbiting-side wrap tooth bottom 6 f and the fixed-side wrap tooth bottom if are formed on the wrap-forming surface of the orbiting-side plate 6 b of the orbiting scroll 6 and the wrap-forming surface of the fixed-side plate 5 b of the fixed scroll 5 , respectively so that each step becomes deeper from the outer periphery toward the inner periphery.
  • FIG. 6 shows each depth of the orbiting-side wrap tooth bottom 6 f and the fixed-side wrap tooth bottom 5 f according to the embodiment.
  • the step difference between the part (a) and the part (c) of the orbiting-side wrap tooth bottom 6 f, and the step difference between the part (a) and the part (c) of the fixed-side wrap tooth bottom 5 f are equally set by the depth ranging from 0.02% to 0.04% of the corresponding wrap tooth height.
  • the step difference between the part (b) and the part (c) of the orbiting-side wrap tooth bottom 6 f, and the step difference between the part (b) and the part (c) of the fixed-side wrap tooth bottom 5 f are equally set by the depth ranging from 0.005% to 0.02% of the corresponding wrap tooth height.
  • the step difference between the part (a) and the part (c) of the orbiting-side wrap tooth bottom 6 f is made smaller than the step difference between the part (a) and the part (c) of the fixed-side wrap tooth bottom 5 f.
  • the step difference between the part (a) and the part (c) of the orbiting-side wrap tooth bottom 6 f is formed to have the resultant depth ranging from 0.005% to 0.02% of the orbiting-side wrap tooth height 6 h.
  • hs the gap between the fixed-side wrap tooth tip 5 e and the orbiting-side wrap tooth bottom 6 f
  • the gap between the fixed-side wrap tooth bottom 5 f and the orbiting-side wrap tooth tip 6 e is referred to as hk
  • Ds the step difference between the part (a) and the part (c) of the orbiting-side wrap tooth bottom 6 f
  • Dk the step difference between the part (a) and the part (c) of the fixed-side wrap tooth bottom 5 f
  • the gap between the fixed-side wrap tooth tip 5 e and the orbiting-side wrap tooth bottom 6 f is defined as hs′
  • the gap between the fixed-side wrap tooth bottom 5 f and the orbiting-side wrap tooth tip 6 e is defined as hk
  • the relationship of hk>hs is established as shown in FIG. 6 .
  • the step difference between the part (a) and the part (c) of the orbiting-side wrap tooth bottom 6 f is defined as Ds′
  • the step difference between the part (a) and the part (c) of the fixed-side wrap tooth bottom 5 f is defined as Dk
  • each difference in the tooth bottom steps of the orbiting scroll 6 and the fixed scroll 5 is individually set in consideration of the applied pressure and thermal deformation which may occur in the orbiting scroll and the fixed scroll.
  • the inner peripheral step difference Ds′ (depth) of the orbiting-side wrap tooth bottom 6 f is made smaller than the inner peripheral step difference Dk (depth) of the fixed-side wrap tooth bottom 5 f so as to improve sealability by eliminating the unnecessary gap, and to suppress the loss caused by leakage of the refrigerant through the gap between the wrap tooth tip and the tooth bottom.
  • the scroll compressor employs the refrigerant as the work fluid especially with lower density than the R410A refrigerant, for example, an R32 refrigerant
  • refrigerant is likely to leak between the adjacent compression chambers because of low density.
  • the R32 refrigerant as the high-temperature refrigerant may have its temperature high during operation. It can be assumed that the gap between the wrap tooth tip and the wrap tooth bottom is widened owing to thermal expansion.
  • the embodiment is configured to have the tooth bottom step that allows suppression of the loss caused by leakage of the refrigerant through the gap between the wrap tooth tip and the tooth bottom. This makes it possible to provide the high-performance scroll compressor even in the case where the single R32 refrigerant is only employed, or it is filled into the refrigeration cycle at a rate of 70% or higher.
  • FIG. 7 schematically shows the structure as the view seen from the direction of the circumferential side of the wrap, representing the relationship between the wrap tooth tip and the tooth bottom.
  • the second embodiment has the same structures as those of the first embodiment except the planar shape to be formed on the opposite surfaces of the wraps of the orbiting scroll 6 and the fixed scroll 5 . Explanations of the components with the same functions will be omitted.
  • each of the parts (b) and (a) of the orbiting-side wrap tooth bottom 6 f of the scroll compressor as shown in FIG. 5 has the same depth so that the orbiting-side wrap tooth bottom 6 f has two steps to eliminate the gab between the orbiting-side wrap tooth bottom 6 f at the winding start side as the deepest position and the fixed-side wrap tooth tip 5 e.
  • the fixed-side wrap tooth bottom 5 f has two steps
  • the orbiting-side wrap tooth bottom 6 f has the single step so that the innermost peripheral step difference Dk of the fixed-side wrap tooth bottom 5 f is made deeper than the inner peripheral step difference Ds′ of the orbiting-side wrap tooth bottom 6 f.
  • Ds′ of the inner peripheral step of the orbiting-side wrap tooth bottom 6 f substantially the same as the depth (at the part (b) at the second deepest position of the fixed-side wrap tooth bottom 5 f.
  • This embodiment provides the similar advantageous effects to those derived from the first embodiment.
  • the embodiment is capable of reducing the manufacturing cost and time by decreasing man-hours for machining the steps decreased in comparison with the first embodiment.
  • This embodiment is configured that the stepped portion from the part (b) to the part (c) is made perpendicular to the fixed-side wrap tooth tip 5 e as shown in FIG. 7 .
  • it is possible to form the slope which inclines from the part (b) to the part (c) so as to change the depth smoothly. This makes it possible to reduce leakage of the refrigerant through the gap generated at the part (c) of the step.
  • the circumferential step of the orbiting-side wrap tooth bottom 6 f may be easily subjected to high-precision machining with the end mill.
  • the aforementioned structure of this embodiment is applicable to any of the embodiments.
  • FIG. 8 schematically shows the structure as the view seen from the direction of the circumferential side of the wrap, representing the relationship between the wrap tooth tip and the tooth bottom.
  • This embodiment has the same structures as those of the first embodiment except the planar shape to be formed on the opposite surfaces of the wraps of the orbiting scroll 6 and the fixed scroll 5 . Explanations of the components with the same functions will be omitted.
  • the depth Ds′ as the step difference at the innermost periphery of the orbiting-side wrap tooth bottom 6 f is approximately half the depth of the step difference Dk as the deepest part of the fixed-side wrap tooth bottom 5 f.
  • This embodiment also provides substantially the same advantageous effects as those of the first or the second embodiment.
  • the depth of the tooth bottom at the orbiting scroll side is set to be half the depth of the tooth bottom at the fixed scroll side, the cutting amount through machining may be reduced, thus decreasing the machining time and prolonging life of the tool.
  • This embodiment has the same structures as those of the first to the third embodiments except the use of the ferrite magnet electric motor formed by embedding the ferrite magnet in the rotor of the electric motor 3 of the scroll compressor. Explanations of the components with the same functions will be omitted.
  • the compressor that employs the ferrite magnet motor is expected to greatly reduce the cost.
  • the use of the ferrite magnet motor has the problem of lower efficiency especially in the low speed region compared with the neodymium magnet motor.
  • Application of the first to the fourth embodiments allows the step size (depth) of the tooth bottom 6 f of the orbiting scroll 6 to be smaller than the step size (depth) of the tooth bottom 5 f of the fixed scroll 5 . This makes it possible to improve sealability, and reduce the loss caused by leakage of the refrigerant through the gap between the wrap tooth tip and the tooth bottom, providing the highly efficient scroll compressor at a low cost even in the low-speed region.
  • This embodiment has the same structures as those of the first to the fourth embodiments except employment of only the single R32 refrigerant in the scroll compressor. Explanations of the components with the same functions will be omitted.
  • the global warming potential (GWP) of the R32 refrigerant is 675 which is approximately one third of the R410A, thus delivering less burden on the environment. Compared with the refrigerant such as the R410A, it exhibits lower density, and is likely to leak from the sealed space. Furthermore, the use of the R32 refrigerant may increase the operation temperature, which tends to deform the wrap under the thermal influence, thus widening the gap between the tooth tip and the tooth bottom.
  • the single R32 refrigerant is only employed or filled into the refrigeration cycle at a rate of approximately 70% or higher through application of the first to the fourth embodiments. Then the step size (depth) of the tooth bottom 6 f of the orbiting scroll 6 is made smaller than the step size (depth) of the tooth bottom 5 f of the fixed scroll 5 so as to improve sealability by eliminating the unnecessary gap, and to reduce the loss caused by leakage of the refrigerant from the gap between the wrap tooth tip and the tooth bottom. This makes it possible to provide the highly efficient scroll compressor while using the 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)
US14/768,958 2013-03-29 2013-03-29 Scroll Compressor Abandoned US20160003247A1 (en)

Applications Claiming Priority (1)

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PCT/JP2013/059444 WO2014155646A1 (fr) 2013-03-29 2013-03-29 Compresseur à spirales

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US20160003247A1 true US20160003247A1 (en) 2016-01-07

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US (1) US20160003247A1 (fr)
EP (1) EP2980408A4 (fr)
JP (1) JP6081577B2 (fr)
CN (1) CN105074218B (fr)
WO (1) WO2014155646A1 (fr)

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US20160348677A1 (en) * 2014-01-22 2016-12-01 Hitachi Appliance, Inc. Scroll compressor
US10502209B2 (en) 2016-01-26 2019-12-10 Daikin Industries, Ltd. Scroll compressor and air conditioning apparatus including the same
US11015600B2 (en) * 2016-02-10 2021-05-25 Mitsubishi Electric Corporation Scroll compressor having sub-discharge port with involute-shaped opening
US11047384B2 (en) 2016-07-06 2021-06-29 Daikin Industries, Ltd. Scroll compressor with non-uniform gap
EP4047208A4 (fr) * 2019-10-15 2022-11-02 Mitsubishi Electric Corporation Compresseur à spirale

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JP2018003762A (ja) * 2016-07-06 2018-01-11 ダイキン工業株式会社 スクロール圧縮機
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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US11015600B2 (en) * 2016-02-10 2021-05-25 Mitsubishi Electric Corporation Scroll compressor having sub-discharge port with involute-shaped opening
US11047384B2 (en) 2016-07-06 2021-06-29 Daikin Industries, Ltd. Scroll compressor with non-uniform gap
EP4047208A4 (fr) * 2019-10-15 2022-11-02 Mitsubishi Electric Corporation Compresseur à spirale

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JPWO2014155646A1 (ja) 2017-02-16
EP2980408A1 (fr) 2016-02-03
EP2980408A4 (fr) 2016-12-21
CN105074218B (zh) 2017-10-13
CN105074218A (zh) 2015-11-18
JP6081577B2 (ja) 2017-02-15
WO2014155646A1 (fr) 2014-10-02

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