WO2021054241A1 - スクロール圧縮機 - Google Patents

スクロール圧縮機 Download PDF

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Publication number
WO2021054241A1
WO2021054241A1 PCT/JP2020/034308 JP2020034308W WO2021054241A1 WO 2021054241 A1 WO2021054241 A1 WO 2021054241A1 JP 2020034308 W JP2020034308 W JP 2020034308W WO 2021054241 A1 WO2021054241 A1 WO 2021054241A1
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WO
WIPO (PCT)
Prior art keywords
scroll
end plate
swing
plate
housing
Prior art date
Application number
PCT/JP2020/034308
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
貞光 塚越
俊一郎 本橋
Original Assignee
株式会社ヴァレオジャパン
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社ヴァレオジャパン filed Critical 株式会社ヴァレオジャパン
Priority to EP20864917.8A priority Critical patent/EP4033101A4/en
Priority to JP2021546639A priority patent/JP7620557B2/ja
Priority to CN202080064354.6A priority patent/CN114402139B/zh
Publication of WO2021054241A1 publication Critical patent/WO2021054241A1/ja

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • F01C17/063—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with only rolling movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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
    • F04C2230/605—Balancing
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/807—Balance weight, counterweight

Definitions

  • the present invention relates to an improved technique for a scroll compressor.
  • the scroll compressor is equipped with a rotation prevention mechanism to prevent the rotation of the swing scroll (also called a turning scroll).
  • a rotation prevention mechanism to prevent the rotation of the swing scroll (also called a turning scroll).
  • an oldam type rotation prevention mechanism that employs an oldam ring has been widely used.
  • the Oldam type rotation prevention mechanism is similar to the principle of the Oldam joint, and the Oldam ring is interposed between the plate surface of the rocking end plate of the rocking scroll and the wall surface of the housing facing the plate surface.
  • the old dam ring is an annular member centered on a drive shaft that drives the swing scroll, and is provided so as to be able to reciprocate only in the direction of a first straight line orthogonal to the drive shaft.
  • the swing scroll is provided so as to be able to reciprocate only in the direction of the second straight line orthogonal to the drive axis with respect to the old dam ring.
  • the direction of the first straight line is deviated by 90 ° from the direction of the second straight line. Therefore, the swing scroll can revolve with respect to the axis of the drive shaft while being restricted from rotating.
  • the pin-and-ring type rotation prevention mechanism known in Patent Document 1 is composed of a plurality of pins provided on the fixed side member and a plurality of circular recesses individually engaged with the plurality of pins. ..
  • the plurality of recesses are arranged and formed in the circumferential direction with respect to the plate surface of the swing end plate of the swing scroll.
  • the plurality of pins extend from the wall surface of the housing facing the plate surface of the swing end plate to the inside of the plurality of recesses.
  • the swing scroll only revolves so that the inner peripheral surface of the recess is always in contact with the pin, and does not use a member that reciprocates in the radial direction like the Oldham type rotation prevention mechanism. Therefore, it is advantageous in suppressing the radial vibration of the swing scroll.
  • the swing scroll is as light as possible.
  • An object of the present invention is to provide a technique capable of reducing the weight of a swing scroll in a scroll compressor that employs a pin-and-ring type rotation prevention mechanism.
  • the fixed scroll (70) has a spiral shape that is erected from a fixed end plate (71) that is non-rotatably supported with respect to the housing (20) and one plate surface (71a) of the fixed end plate (71).
  • the oscillating scroll (80) is formed from a disk-shaped oscillating end plate (81) located facing the fixed spiral body (73) and a first plate surface (81a) of the oscillating end plate (81). It has a spiral swinging spiral body (82) that stands upright toward the fixed spiral body (73) and is combined with the fixed spiral body (73) to form a compression chamber (83).
  • the swinging end plate (81) is rotatably supported by an eccentric shaft (51) provided at one end of the drive shaft (50).
  • the rotation prevention mechanism (90) is The swing end plate (81) is provided on the second plate surface (81b) opposite to the first plate surface (81a) and is arranged in the circumferential direction of the second plate surface (81b).
  • the wall portion (31a) of the swinging end plate (81) facing the second plate surface (81b) extends into the plurality of recesses (91) and extends from the plurality of recesses (91).
  • a scroll compressor (10; 10A; 10B) comprising a plurality of pins (93) that are individually engaged with the inner peripheral surface (91a) of the recess (91) directly or via a ring member (92).
  • the rocking end plate (81) has at least one groove portion (111, 112; 112A; 112B) on the outer peripheral surface (81c) that does not communicate with the first plate surface (81a) and the second plate surface (81b).
  • a scroll compressor characterized by having is provided.
  • the groove portion (112; 112A; 112B) is provided between the plurality of adjacent recesses (91).
  • the groove portion (112; 112A; 112B) is the deepest at a position far from the plurality of adjacent recesses (91).
  • the weight of the swing scroll can be reduced by having at least one groove portion on the outer peripheral surface of the swing end plate that does not communicate with the first plate surface and the second plate surface. Since the groove portion does not communicate with the first plate surface and the second plate surface, it does not affect the first plate surface and the second plate surface. Therefore, it does not interfere with the swinging spiral body erected on the first plate surface, and the second plate surface can be used as a sliding surface up to the vicinity of the outermost circumference.
  • FIG. It is sectional drawing of the scroll compressor according to Example 1.
  • FIG. It is a perspective view of the swing scroll shown in FIG. It is sectional drawing along the axis of the swing scroll shown in FIG. It is the figure which looked at the rocking scroll shown in FIG. 3 from the 1st plate surface side of the rocking end plate.
  • FIG. 3 is a view of the swing scroll shown in FIG. 3 as viewed from the second plate surface side of the swing end plate.
  • FIG. 6 is a sectional view taken along line 6-6 of FIG.
  • FIG. 5 is a cross-sectional view (corresponding to the cross-sectional position of FIG. 6) of the swing scroll of the scroll compressor according to the second embodiment as viewed from the second plate surface side of the swing end plate.
  • FIG. 5 is a cross-sectional view (corresponding to the cross-sectional position of FIG. 6) of the swing scroll of the scroll compressor according to the third embodiment as viewed from the second plate surface side of the swing end plate.
  • the scroll compressor 10 of the first embodiment will be described with reference to FIGS. 1 to 6.
  • the scroll compressor 10 is suitable for use in a refrigeration cycle using a refrigerant as a working fluid, for example, in a refrigeration cycle of an automobile air conditioner.
  • the use of the scroll compressor 10 is not limited.
  • the scroll compressor 10 includes a horizontal housing 20, an electric motor 40 housed in the housing 20, a drive shaft 50 (including an output shaft of the electric motor 40) driven by the electric motor 40, and a drive shaft by the electric motor 40. It is a so-called horizontal electric compressor having a compression mechanism 60 driven via 50.
  • the housing 20 has a horizontal tubular first housing 21 and a second housing 22 that closes one opening of the first housing 21.
  • the inside of the first housing 21 is divided into two in the longitudinal direction by an integral partition wall 23.
  • one of the partition walls 23 is referred to as the first tubular portion 24, and the other is referred to as the second tubular portion 25.
  • the open end of the first tubular portion 24 is closed by the lid 26.
  • Inside the first cylinder portion 24, an inverter device (not shown) for supplying driving power to the electric motor 40 is housed inside the first cylinder portion 24, an inverter device (not shown) for supplying driving power to the electric motor 40 is housed.
  • the second housing 22 is fastened to the first housing 21 by a fastening member (not shown) such as a bolt so as to close the open end of the second tubular portion 25.
  • the housing 20 has a suction port 27 for sucking the refrigerant into the housing 20 from the outside, and a discharge port 28 for discharging the refrigerant compressed by the compression mechanism 60 from the housing 20.
  • the suction port 27 is provided in the second cylinder portion 25.
  • the discharge port 28 is provided in the second housing 22.
  • the electric motor 40, the drive shaft 50, and the compression mechanism 60 are housed in the second cylinder portion 25 of the first housing 21.
  • the compression mechanism 60 is located on the opening side in the second cylinder portion 25. Inside the second tubular portion 25, the space portion 29 between the partition wall 23 and the compression mechanism 60 is hereinafter referred to as a “low pressure chamber 29”.
  • the electric motor 40 is located in the low pressure chamber 29.
  • the low pressure chamber 29 communicates with the suction port 27.
  • a support block 31 is provided between the electric motor 40 and the compression mechanism 60.
  • the support block 31 is restricted from both relative rotation and axial relative movement with respect to the second tubular portion 25. Therefore, it can be considered that the support block 31 constitutes a part of the housing 20.
  • the support block 31 will be described as “a part of the housing 20” as appropriate.
  • the drive shaft 50 is located in the low pressure chamber 29, extends horizontally in the longitudinal direction of the second cylinder portion 25, and penetrates the support block 31 toward the compression mechanism 60.
  • the drive shaft 50 is rotatably supported by a first bearing 32 provided on the partition wall 23 and a second bearing 33 provided on the support block 31.
  • the drive shaft 50 extends horizontally in the longitudinal direction of the housing 20 and is rotatably supported by the housing 20.
  • each of the bearings 32 and 33 is composed of rolling bearings.
  • the drive shaft 50 has an eccentric shaft 51 on one end surface penetrating the support block 31.
  • the eccentric shaft 51 (eccentric pin 51) extends from one end surface of the drive shaft 50 toward the compression mechanism 60 and is parallel to the drive shaft 50.
  • the center line CL2 of the eccentric shaft 51 is offset from the center line CL1 of the drive shaft 50, and an annular bush 52 is rotatably fitted to the eccentric shaft 51.
  • a counter weight 53 (balance weight 53) projecting radially from the bush 52 is integrally provided on a part of the bush 52.
  • a bearing 54 (third bearing 54) is fitted on the outer peripheral surface of the bush 52.
  • the third bearing 54 is preferably composed of a rolling bearing.
  • the inner peripheral surface of the bush 52 fitted to the eccentric shaft 51 and the outer peripheral surface of the bush 52 fitted to the bearing 54 are not coaxial, so that the center line CL3 of the swing scroll 80 becomes the eccentric shaft 51.
  • a well-known self-aligning mechanism that allows the center line CL2 to be located inside the rotation locus formed by the center line CL2 is configured.
  • the electric motor 40 has a rotor 41 fixed to the drive shaft 50 and a stator 42 surrounding the rotor 41.
  • the stator 42 is fixed to the inner peripheral surface of the second tubular portion 25.
  • the drive shaft 50 functions as an output shaft of the electric motor 40.
  • the compression mechanism 60 includes a fixed scroll 70 and a swing scroll 80.
  • the fixed scroll 70 has a disk-shaped fixed end plate 71, a cylindrical outer peripheral wall 72, and a spiral-shaped fixed spiral body 73.
  • the fixed end plate 71 (also referred to as the fixed plate 71) is orthogonal to the center line CL2 of the eccentric shaft 51 and is supported by the housing 20 so as not to rotate relative to each other.
  • the outer peripheral wall 72 is a cylinder erected from the outer edge of one plate surface 71a (the surface 71a facing the electric motor 40) of the fixed end plate 71 over the entire circumference.
  • the fixed spiral body 73 is located inside the outer peripheral wall 72 and stands upright from one plate surface 71a of the fixed end plate 71.
  • the fixed spiral body 73 is configured, for example, in an involute curved shape.
  • a refrigerant suction port 74 for sucking the refrigerant from the outside to the inside is formed on the outer peripheral wall 72 of the fixed scroll 70.
  • the swing scroll 80 is combined with the fixed scroll 70 and revolves with respect to the fixed scroll 70.
  • the swing scroll 80 has a disc-shaped swing end plate 81 located facing the fixed spiral body 73, and a spiral swing spiral body 82.
  • the swing end plate 81 is orthogonal to the center line CL3 of the swing scroll 80 and is located inside the outer peripheral wall 72 of the fixed spiral body 73.
  • the plate surface 81a facing one plate surface 71a of the fixed end plate 71 is referred to as “first plate surface 81a”, and is the surface 81b opposite to the first plate surface 81a. Is referred to as "second plate surface 81b”.
  • the swinging spiral body 82 is erected from the first plate surface 81a of the swinging end plate 81 toward the fixed spiral body 73, and is combined with the fixed spiral body 73 to form a plurality of compression chambers 83.
  • the swinging spiral body 82 is formed in, for example, an involute curved shape (see FIG. 4).
  • a circular recess for being supported 84 is formed at the center CL3 of the swinging end plate 81.
  • the outer peripheral surface of the third bearing 54 (see FIG. 1) is fitted in the supported recess 84.
  • the swing end plate 81 is rotatably supported by an eccentric shaft 51 provided on the drive shaft 50 via a third bearing 54.
  • the swing scroll 80 is driven by the drive shaft 50.
  • the swing scroll 80 can revolve (rotate eccentrically) around the axis CL2 of the drive shaft 50.
  • the scroll compressor 10 has a rotation prevention mechanism 90 that prevents the swing scroll 80 from rotating.
  • the rotation prevention mechanism 90 is a pin-and-ring type rotation prevention mechanism including a plurality of recesses 91 provided in the swing end plate 81 and a plurality of detent pins 93 provided in the housing 20.
  • the recess 91 is referred to as a "pin engaging recess 91”
  • the pin 93 is referred to as a "rotation stop pin 93”.
  • a plurality of (for example, six) pin engaging recesses 91 are arranged at equal pitches along the circumferential direction on the second plate surface 81b of the swing end plate 81. There is. That is, the plurality of pin engaging recesses 91 are perfect circular recesses located at equal pitches on concentric circles with respect to the center CL3 of the swing end plate 81.
  • the plurality of detent pins 93 have a structure of a round bar parallel to the drive shaft 50, and face the second plate surface 81b of the swing end plate 81 in the housing 20 (for example, the support block 31). It extends from the wall portion 31a to the inside of the plurality of pin engaging recesses 91.
  • These plurality of detent pins 93 are individually provided directly on the inner peripheral surface 91a of the plurality of pin engaging recesses 91 or via a ring member 92 (member 92 described by an imaginary line in FIG. 3). Engaged. Therefore, the swing scroll 80 can move with respect to the housing 20 only within the range of the inner peripheral surface 91a of the plurality of circular pin engaging recesses 91.
  • the swing scroll 80 tries to rotate with the rotation of the drive shaft 50, but the rotation is regulated by the pin engaging recess 91 and the detent pin 93. In this way, the rotation prevention mechanism 90 can prevent the rotation movement while allowing the revolution movement of the swing scroll 80.
  • the rotation of the swing scroll 80 is prevented by engaging the plurality of detent pins 93 with the inner peripheral surfaces 91a of the plurality of pin engagement recesses 91.
  • the swing scroll 80 since the swing scroll 80 has a predetermined mass, a radial excitation force is generated due to the revolution of the swing scroll 80, but the radial excitation force due to the revolution of the swing scroll 80 is eccentric.
  • the counter weight 53 provided on the shaft 51 balances the weight.
  • the swing end plate 81 of the swing scroll 80 has an annular sliding contact portion 101 and a plurality of recesses 102 for adjusting the center of gravity on the second plate surface 81b.
  • the annular sliding contact portion 101 is a flat, constant-width annular surface slightly protruding from the outer peripheral edge of the second plate surface 81b.
  • the annular sliding contact portion 101 can be slidably contacted with the wall surface of the wall portion 31a of the support block 31 (that is, the wall surface of the housing 20) when the swing scroll 80 revolves.
  • the plurality of recesses 102 for adjusting the center of gravity are recessed from the second plate surface 81b so as to adjust the position of the center of gravity of the swing scroll 80, and are located radially inside the annular sliding contact portion 101. ..
  • These center-of-gravity adjusting recesses 102 are in the range from the winding end end 82a (base point Sp) of the swinging spiral body 82 shown in FIG. 4 to the spiral angle ⁇ (about 180 °) in front of it, and It is arranged in the middle of the pin engaging recess 91 adjacent to the pin engaging recess 91.
  • the mass of the swing scroll 80 in the region ⁇ corresponding to the winding end side of the swing spiral body 82 can be brought close to the mass of the swing scroll 80 in the other regions. it can.
  • the center of gravity of the swing scroll 80 can be aligned with the center CL3 of the swing end plate 81.
  • a plurality of straight lines L1 and a plurality of straight lines extending radially from the center CL3 of the swing end plate 81 When the swing scroll 80 is viewed from the second plate surface 81b side of the swing end plate 81, a plurality of straight lines L1 and a plurality of straight lines extending radially from the center CL3 of the swing end plate 81.
  • L2 the plurality of straight lines L1 and the plurality of straight lines L2 will be described separately by distinguishing them into a plurality of first straight lines L1 and a plurality of second straight lines L2.
  • the plurality of first straight lines L1 are straight lines passing through the center of each pin engaging recess 91.
  • the plurality of second straight lines L2 are straight lines passing between the adjacent pin engaging recesses 91 and 91. All straight lines L1 and L2 are arranged at equal angles.
  • the inner peripheral surface 91a of the pin engaging recess 91 and the inner peripheral surface of the annular sliding contact portion 101 match at the position of the first straight line L1.
  • the plurality of recesses 102 for adjusting the center of gravity are located on the second straight line L2.
  • the surface 102b near the annular sliding contact portion 101 is a straight line orthogonal to the second straight line L2 and is close to the annular sliding contact portion 101. ..
  • the thickness (first thickness) from the outer peripheral surface 81c of the swing end plate 81 to the inner peripheral surface 91a of the pin engaging recess 91 on the first straight line L1 is Th1.
  • the thickness (second thickness) from the surface 102b near the annular sliding contact portion 101 to the outer peripheral surface 81c of the swing end plate 81 in the inner peripheral surface 102a of the center of gravity adjusting recess 102. ) Is Th2, which is thicker than the first thickness Th1 (Th2> Th1).
  • the swing end plate 81 has at least one groove 111 and / or groove 112 that does not communicate with the outer peripheral surface 81c and the first plate surface 81a and the second plate surface 81b.
  • it has a first groove portion 111 and / or a second groove portion 112.
  • the first groove portion 111 and the second groove portion 112 have a U-shaped cross section (see FIG. 3) in which the outer peripheral surface 81c side of the swing end plate 81 is opened.
  • the first groove portion 111 includes a groove bottom surface 111a on the center CL3 side of the swing end plate 81, and a pair of flat groove side surfaces 111b and groove side surfaces 111b from the groove bottom surface 111a toward the outer peripheral surface 81c.
  • the second groove portion 112 includes a groove bottom surface 112a on the center CL3 side of the swing end plate 81, and a pair of flat groove side surfaces 112b and groove side surfaces 112b extending from the groove bottom surface 112a toward the outer peripheral surface 81c.
  • the plurality of first groove portions 111 are located on the outer peripheral surface 81c of the swing end plate 81 at positions facing each pin engaging recess 91, that is, on each first straight line L1.
  • Each first groove portion 111 is an arc-shaped groove along the outer peripheral surface 81c. Therefore, the groove bottom surface 111a is an arcuate surface along the outer peripheral surface 81c.
  • each first groove portion 111 is recessed to the vicinity of the pin engaging recess 91.
  • the first thickness Th1 from the outer peripheral surface 81c of the swing end plate 81 to the inner peripheral surface 91a of the pin engaging recess 91 is relatively small. Therefore, on the first straight line L1, the depth De1 (first groove depth De1) from the outer peripheral surface 81c of the swing end plate 81 to the groove bottom surface 111a of each first groove portion 111 is relatively small.
  • the plurality of second groove portions 112 are provided between the plurality of pin engaging recesses 91 and the adjacent pin engaging recesses 91 in the outer peripheral surface 81c of the swing end plate 81.
  • the plurality of second groove portions 112 are arranged in the middle of the pin engaging recess 91 and the adjacent pin engaging recess 91, respectively. More specifically, when the swing end plate 81 is viewed from the center CL3 direction (second plate surface 81b side), each of the second groove portions 112 is located on the second straight line L2 and with respect to the second straight line L2. It is a linear groove that is orthogonal to each other. Therefore, the groove bottom surface 112b is a linear surface orthogonal to the second straight line L2.
  • each second groove portion 112 is recessed to the vicinity of the center of gravity adjusting recess 102. Therefore, each second groove portion 112 is deepest at a position P1 far from the pin engaging recess 91 adjacent to the pin engaging recess 91, that is, at a position P1 intersecting the second straight line L2.
  • each second groove portion 112 has the largest depth De2 (second groove depth De2) from the outer peripheral surface 81c of the swing end plate 81 to the groove bottom surface 112a on the second straight line L2.
  • the second groove depth De2 is larger than the first groove depth De1 (De2> De1).
  • the outline of the operation of the scroll compressor 10 is as follows. As shown in FIG. 1, the swing scroll 80 revolves when the drive shaft 50 is driven by the electric motor 40. As a result, the refrigerant sucked from the suction port 27 and the refrigerant in the low pressure chamber 29 enter the compression chamber 83 through the refrigerant suction port 74 of the fixed scroll 70. As the swing scroll 80 revolves, the compression chamber 83 gradually moves toward the center while reducing the internal volume, whereby the refrigerant in the compression chamber 83 is compressed. As the pressure in the compression chamber 83 increases, the check valve 121 opens, and the compressed refrigerant flows into the discharge chamber 122 in the second housing 22 and enters the adjacent gas-liquid separation chamber 123. The gaseous refrigerant whose oil has been separated by the gas-liquid separation chamber 124 is discharged outward from the discharge port 28.
  • the weight of the swing scroll 80 can be reduced by having at least one groove 111 and / or groove 112 on the outer peripheral surface 81c of the swing end plate 81. it can. Further, it is possible to reduce the weight and size of the counter weight 53 for balancing with the exciting force accompanying the revolution of the swing scroll 80. Further, since the groove portions 111 and 112 do not communicate with the first plate surface 81a and the second plate surface 81b, they do not affect the first plate surface 81a and the second plate surface 81b. Therefore, the groove portions 111 and 112 do not interfere with the swinging spiral body 82 erected on the first plate surface 81a. Moreover, the second plate surface 81b can be used as a sliding surface (annular sliding contact portion 101) with respect to the wall surface of the housing 20 up to the vicinity of the outermost periphery.
  • the groove portion 112 (second groove portion 112) is provided between the pin engaging recesses 91 and 91 (the pin engaging recess 91 and the adjacent pin engaging recess 91) adjacent to each other. Has been done.
  • a deeper groove having a second groove depth De2 can be formed while avoiding interference with each pin engaging recess 91. it can.
  • the weight of the swing scroll 80 can be further reduced.
  • each groove 112 can be arranged at an optimum position in the swing scroll 80. Further, each groove portion 112 can be freely arranged only in a necessary portion at a position where it does not interfere with the pin engaging recess 91. Therefore, it is easy to balance the weight of the swing scroll 80 itself by the groove 112. The swing scroll 80 does not become large in order to balance the weight. Therefore, the degree of freedom in designing each groove 112 can be increased. In this way, it is possible to achieve both the weight reduction of the swing scroll 80 and the weight balance of the swing scroll 80 itself.
  • the groove portion 112 (second groove portion 112) is the deepest at the position P1 far from the plurality of adjacent pin engaging recesses 91 (pin engaging recesses 91 adjacent to the pin engaging recesses 91). The farther the outer peripheral surface 81c of the swing end plate 81 is from the adjacent pin engaging recesses 91, 91, the more the groove bottom surface 112a of each groove 112 does not interfere with the pin engaging recesses 91, 91. Based on this, the depth De2 (second groove depth De2) of each groove portion 112 was maximized at the position P1 far from the position of the recess 91. Therefore, the swing scroll 80 can be further reduced in weight.
  • the swing scroll 80 is fixed (grasped) to the fixing base of the processing machine by a fixing claw such as a chuck or a clamper (not shown).
  • a fixing claw such as a chuck or a clamper (not shown).
  • the fixing claws can be easily and surely fixed to a fixing base such as a bed or a table.
  • the groove portion 111 or the groove portion 112 is located in the outer peripheral surface 81c of the swing end plate 81 at a position (on the second straight line L2) avoiding the recess 91.
  • the swing scroll 80 can be fixed in the swing axis direction by effectively utilizing the groove side surface 111b or the groove side 112b of the groove 111 or the groove 112 and hooking the fixing claw. Therefore, the fixed claw can be hooked without causing distortion in the swing scroll 80 having a relatively low rigidity.
  • FIG. 7 shows a cross-sectional configuration of the swing scroll 80A of the scroll compressor 10A according to the second embodiment as viewed from the second plate surface 81b side of the swing end plate 81, and corresponds to the cross-sectional position of FIG.
  • the scroll compressor 10A of the second embodiment is characterized in that the second groove portion 112 of the first embodiment shown in FIGS. 1 to 6 is changed to the second groove portion 112A shown in FIG. 7.
  • Other basic configurations are the same as those of the scroll compressor 10 according to the first embodiment.
  • reference numerals are used and detailed description thereof will be omitted.
  • the second groove portion 112A of the second embodiment has a configuration in which the outer peripheral surface 81c side of the swinging end plate 81 is opened as in the first embodiment, and the groove bottom surface 112a on the center CL3 side of the swinging end plate 81 and this groove. It is composed of a pair of flat groove side surfaces 112b extending from the bottom surface 112a to the outer peripheral surface 81c. More specifically, as shown in FIG. 7, when the swing end plate 81 is viewed from the central CL3 direction (second plate surface 81b side), each second groove portion 112A is a circle from the outer peripheral surface 81c of the swing end plate 81. It is dented in an arc shape. Therefore, the groove bottom surface 112b is also an arcuate surface recessed in an arc shape from the outer peripheral surface 81c of the swing end plate 81.
  • each second groove portion 112A is recessed to the vicinity of the center of gravity adjusting recess 102. Therefore, each of the second groove portions 112A is deepest at a position P1 far from the pin engaging recesses 91 adjacent to the plurality of pin engaging recesses 91, that is, at a position P1 intersecting the second straight line L2.
  • each second groove portion 112A has the largest depth De2A (second groove depth De2A) from the outer peripheral surface 81c of the swing end plate 81 to the groove bottom surface 112a on the second straight line L2.
  • the scroll compressor 10A according to the second embodiment can exhibit the same effect as that of the first embodiment.
  • the surface 102b near the annular sliding contact portion 101 may be an arc-shaped surface along the groove bottom surface 112a of the second groove portion 112A.
  • the second groove depth De2A can be set larger than the second groove depth De2 of the first embodiment shown in FIG. 6 above.
  • FIG. 8 shows a cross-sectional configuration of the swing scroll 80B of the scroll compressor 10B according to the third embodiment as viewed from the second plate surface 81b side of the swing end plate 81, and corresponds to the cross-sectional position of FIG.
  • the scroll compressor 10B of the third embodiment is characterized in that the second groove portion 112 of the first embodiment shown in FIGS. 1 to 6 is changed to the second groove portion 112B shown in FIG.
  • Other basic configurations are the same as those of the scroll compressor 10 according to the first embodiment.
  • reference numerals are used and detailed description thereof will be omitted.
  • the second groove portion 112B of the third embodiment has a configuration in which the outer peripheral surface 81c side of the swinging end plate 81 is opened as in the first embodiment, and the groove bottom surface 112a on the center CL3 side of the swinging end plate 81 and this groove. It is composed of a pair of flat groove side surfaces 112b extending from the bottom surface 112a to the outer peripheral surface 81c. More specifically, as shown in FIG. 8, when the swing end plate 81 is viewed from the center CL1 direction (second plate surface 81b side), each second groove portion 112B is rectangular from the outer peripheral surface 81c of the swing end plate 81. It is dented in shape. Therefore, the groove bottom surface 112b is a linear surface orthogonal to the second straight line L2.
  • each second groove portion 112B is recessed to the vicinity of the center of gravity adjusting recess 102. Therefore, each second groove portion 112B is deepest at a position P1 far from the pin engaging recesses 91 adjacent to the plurality of pin engaging recesses 91, that is, at a position P1 intersecting the second straight line L2.
  • the scroll compressor 10B according to the third embodiment can exhibit the same effect as that of the first embodiment.
  • the scroll compressors 10; 10A; 10B according to the present invention are not limited to the examples as long as they exhibit the actions and effects of the present invention.
  • the scroll compressors 10; 10A; 10B are not limited to the horizontal electric compressor, and the drive shaft 50 may be driven by an external power source.
  • a belt-driven scroll compressor that transmits engine power to a pulley provided on the drive shaft 50 by a belt can be used.
  • the swing scroll 80 is not limited to a configuration having an annular sliding contact portion 101 and a recess 102 for adjusting the center of gravity.
  • the shapes and sizes of the groove portions 111, 112; 112A; 112B are not limited to the above Examples 1 to 3, and can be set arbitrarily.
  • each of the groove portions 111, 112; 112A; 112B need only have at least one of the outer peripheral surfaces 81c of the swing end plate 81.
  • the scroll compressor 10; 10A; 10B of the present invention is suitable for use in the refrigeration cycle of a vehicle air conditioner.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2020/034308 2019-09-20 2020-09-10 スクロール圧縮機 WO2021054241A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP20864917.8A EP4033101A4 (en) 2019-09-20 2020-09-10 SPIRAL COMPRESSOR
JP2021546639A JP7620557B2 (ja) 2019-09-20 2020-09-10 スクロール圧縮機
CN202080064354.6A CN114402139B (zh) 2019-09-20 2020-09-10 涡旋式压缩机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019-171828 2019-09-20
JP2019171828 2019-09-20

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WO2021054241A1 true WO2021054241A1 (ja) 2021-03-25

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EP (1) EP4033101A4 (enrdf_load_stackoverflow)
JP (1) JP7620557B2 (enrdf_load_stackoverflow)
CN (1) CN114402139B (enrdf_load_stackoverflow)
WO (1) WO2021054241A1 (enrdf_load_stackoverflow)

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US20230400023A1 (en) * 2022-06-09 2023-12-14 Hanon Systems Orbit scroll platter mass reduction

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CN116816680A (zh) * 2022-10-28 2023-09-29 杭州绿能新能源汽车部件有限公司 具有排气分油结构的压缩机
DE102024124885A1 (de) 2023-09-22 2025-03-27 Hanon Systems Scroll-Verdichter zum Verdichten eines gasförmigen Fluids

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WO2023239084A1 (en) * 2022-06-09 2023-12-14 Hanon Systems Orbit scroll platter mass reduction
US12117000B2 (en) * 2022-06-09 2024-10-15 Hanon Systems Orbiting scroll platter mass reduction

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JPWO2021054241A1 (enrdf_load_stackoverflow) 2021-03-25
JP7620557B2 (ja) 2025-01-23
EP4033101A1 (en) 2022-07-27
EP4033101A4 (en) 2023-08-16
CN114402139B (zh) 2024-01-30
CN114402139A (zh) 2022-04-26

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