WO2015122111A1 - 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
WO2015122111A1
WO2015122111A1 PCT/JP2015/000060 JP2015000060W WO2015122111A1 WO 2015122111 A1 WO2015122111 A1 WO 2015122111A1 JP 2015000060 W JP2015000060 W JP 2015000060W WO 2015122111 A1 WO2015122111 A1 WO 2015122111A1
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WO
WIPO (PCT)
Prior art keywords
bearing
scroll
pin
scroll compressor
compressor according
Prior art date
Application number
PCT/JP2015/000060
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
創 佐藤
隆 作田
Original Assignee
三菱重工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Publication of WO2015122111A1 publication Critical patent/WO2015122111A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • F01C17/066—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with an intermediate piece sliding along perpendicular axes, e.g. Oldham coupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • F04C18/0284—Details of the wrap tips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • 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
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof
    • 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
    • F04C29/04—Heating; Cooling; Heat insulation

Definitions

  • the present invention relates to a rotation preventing mechanism of a scroll compressor.
  • the scroll compressor includes a fixed scroll and a orbiting scroll.
  • the fixed scroll and the orbiting scroll are both provided with a spiral wrap on one side of the disk-shaped end plate.
  • the fixed scroll and the orbiting scroll are opposed to each other in a state where the wraps are engaged, and the orbiting scroll is revolved with respect to the stationary scroll. Then, the volume of the compression space formed between the two scrolls is reduced as the orbiting scroll turns, thereby compressing the fluid in the space.
  • a crank pin type anti-rotation mechanism is known as a mechanism for preventing rotation of the orbiting scroll.
  • the crank pin type anti-rotation mechanism supports the crank pin by the bearing, but provides a predetermined clearance between the bearing and the bearing box or between the crank pin and the bearing, and between the bearing and the bearing box or the crank Between the pin and the bearing, an elastic member filling the clearance, typically an O-ring, is interposed (for example, Patent Document 1 and Patent Document 2).
  • an elastic member filling the clearance typically an O-ring
  • Patent Document 1 and Patent Document 2 There are several reasons for adopting such a configuration in which the clearance is provided and the elastic member is interposed there, and one of the reasons is the thermal expansion of the orbiting scroll caused by the compression of the fluid. That is, damage to the orbiting scroll due to thermal expansion is prevented by absorbing the displacement of the crank pin in the radial direction of the orbiting scroll due to thermal expansion of the orbiting scroll by the O ring which is an elastic body.
  • the predetermined clearance is provided in the entire circumferential direction corresponding to the O-ring, so the clearance is not only in the radial direction of the orbiting scroll but also in the circumferential direction. It will exist. Therefore, when the crank pin is displaced in the circumferential direction, the orbiting scroll is displaced in the circumferential direction along with this displacement, and a twist is generated between the orbiting scroll and the fixed scroll. Due to this twisting, the fluid can not be compressed properly, and there is a possibility that the wrap of the orbiting scroll and the wrap of the fixed scroll may be in too strong contact and damaged.
  • the present invention is made based on such a subject, and an object of the present invention is to provide a scroll compressor which can absorb displacement of a revolving scroll due to thermal expansion and can prevent twisting of the revolving scroll.
  • the scroll compressor of the present invention which has been made for this purpose, is combined to form a compression space which is capable of orbiting the fixed scroll and the fixed scroll while compressing fluid between the fixed scroll and the fixed scroll.
  • the rotating scroll and the rotation preventing mechanism of the rotating scroll are provided.
  • the anti-rotation mechanism includes a pin crank having a first pin and a second pin, a first bearing which is held by a bearing box integral with the orbiting scroll and supports the first pin, and a second bearing provided in the vicinity of the bearing box. And a second bearing supported by the bearing accommodation space or the fixed scroll and supporting the second pin.
  • the rotation prevention mechanism satisfies the above equation (1), so that the displacement in the circumferential direction can be reduced. Therefore, according to the scroll compressor of the present invention, in addition to being able to absorb the displacement of the crankpin in the radial direction due to the thermal expansion of the orbiting scroll, it is possible to prevent the twisting of the orbiting scroll.
  • the opening of the bearing housing holding the bearing has a shape having a major axis in the radial direction and a minor axis in the circumferential direction.
  • the first form is different from the second form and the third form in that the purpose is achieved by specifying the shape of the bearing housing.
  • an elastic member such as an O-ring is not hindered.
  • the second and third embodiments identify the shape of the elastic member provided between the first bearing and the bearing housing or between the first pin and the bearing housing.
  • the second embodiment when the thickness in the radial direction is tr and the thickness in the circumferential direction is t ⁇ , tr ⁇ t ⁇ formula (2) Use an elastic member that satisfies
  • the elastic coefficient in the radial direction when the elastic coefficient in the radial direction is Er and the elastic coefficient in the circumferential direction is E ⁇ , Er ⁇ E ⁇ ...
  • Formula (3) Use an elastic member that satisfies
  • the displacement allowance of the first pin in the radial direction can be increased, while the displacement allowance of the first pin in the circumferential direction can be reduced. Therefore, the scroll compressor according to the first to third embodiments can prevent the twisting of the orbiting scroll in addition to the ability to absorb the displacement of the crankpin in the radial direction due to the thermal expansion of the orbiting scroll. Further, in the scroll compressors according to the second and third embodiments, the bearing box can be easily processed because it is not necessary to process the opening of the bearing box into, for example, an oval having a major axis and a minor axis.
  • the twisting of the orbiting scroll in addition to allowing the displacement of the crankpin in the radial direction due to the thermal expansion of the orbiting scroll, the twisting of the orbiting scroll can be prevented.
  • (A) is a perspective view which shows the lap
  • (b) is a perspective view which shows the lap
  • the scroll compressor 1 As shown in FIGS. 1 and 2, the scroll compressor 1 according to the present embodiment is pivoted into a housing 10 forming an outer shell of the scroll compressor 1, a fixed scroll 20 fixed to the housing 10, and the housing 10.
  • An orbiting scroll 30 which can be accommodated is provided as a main component.
  • These main components are formed of metal materials such as aluminum-based alloys and iron-based alloys.
  • the scroll compressor 1 is a scroll compressor of a type called 3D scroll (registered trademark) capable of obtaining a high compression ratio by compressing a fluid not only in the circumferential direction but also in the height direction.
  • the housing 10 is a sealed container comprising a first housing 10a and a second housing 10b as shown in FIG.
  • the first housing 10 a is fixed to the fixed scroll 20 and accommodates the cooling fins 24 of the fixed scroll 20 therein.
  • the first housing 10 a includes a discharge port 12 that discharges the compressed fluid discharged from the discharge port 21 e of the fixed scroll 20 to the outside.
  • the second housing 10 b accommodates and holds the orbiting scroll 30, the rotation preventing mechanism 40, and the drive shaft 50 inside the accommodation chamber 11 b.
  • the second housing 10 b includes a storage chamber 11 c for storing the second element 45 of the rotation preventing mechanism 40 and a storage chamber 11 d for storing the drive shaft 50 and the main bearing 54 in the storage chamber 11 b.
  • the fixed scroll 20 has an end plate 21 formed in a substantially disc shape, a spiral wrap 22 provided on one surface side of the end plate 21, and the other surface of the end plate 21.
  • a cooling fin 24 provided on the side and an outer peripheral wall 26 surrounding the outermost periphery of the fixed scroll 20 are integrally formed, for example, by casting an aluminum alloy.
  • the outer peripheral wall 26 is provided with a suction port 27 for sucking a fluid to be compressed.
  • the outer peripheral wall 26 is exposed to the outside and constitutes a part of the housing 10.
  • the side on which the wrap 22 is provided is referred to as the front
  • the side on which the cooling fins 24 are provided is referred to as the back.
  • the low step 21a and the high step 21b are provided on the end plate 21 so that the height of the back of the wrap 22 is lower on the inner circumferential side than on the outer circumferential side.
  • the wrap 22 formed on the top 21a is tall, and the wrap 22 formed on the high step 21b is short.
  • step difference of the boundary of the low step part 21a and the high step part 21b has appeared also in the back of the end plate 21.
  • the wrap 22 is provided at its tip end with a self-lubricating tip seal 23 which contacts the front side of the end plate 31 of the orbiting scroll 30 to seal the compression chamber.
  • the end plate 21 is formed with a discharge port 21e penetrating the front and back, and the fluid compressed by the fixed scroll 20 and the orbiting scroll 30 is discharged from the discharge port 12 to the outside through the discharge port 21e.
  • a plurality of cooling fins 24 are provided on the back surface of the end plate 21, and the fixed scroll 20 is cooled by the outside air flowing from an opening (not shown) formed in the housing 10 passing through the cooling fins 24.
  • the plurality of plate-shaped cooling fins 24 are formed to face the same direction, but, for example, the plurality of cooling fins 24 may be provided radially from the center of the end plate 21. The same applies to the orbiting scroll 30.
  • the orbiting scroll 30 has an end plate 31 formed in a substantially disc shape, a spiral wrap 32 provided on one surface side of the end plate 31, and the other surface of the end plate 31. It has cooling fins 34 provided on the side, and is integrally formed, for example, by casting an aluminum alloy.
  • the side on which the wrap 32 is provided is referred to as the front, and the side on which the cooling fins 34 are provided is referred to as the back.
  • the wrap 32 of the orbiting scroll 30 corresponds to the wrap 22 of the fixed scroll 20, and is formed such that its height is lower on the inner peripheral side than on the outer peripheral side.
  • the end plate 31 is provided with a low step 31a and a high step 31b, and the wrap 32 formed on the low step 31a is tall and the wrap 32 formed on the high step 21b is tall Low.
  • step difference of the boundary of the low step part 31a and the high step part 31b has appeared also in the back of the end plate 31, and the concave groove 31c which recedes toward the front is formed in the said part.
  • the wrap 32 is provided at its tip end with a self-lubricating tip seal 33 which contacts the front side of the end plate 21 of the fixed scroll 20 to seal the compression chamber.
  • a plurality of cooling fins 34 are provided on the back surface of the end plate 31 and cools the orbiting scroll 30 by the outside air flowing from an opening (not shown) formed in the housing 10 passing through the cooling fins 34. .
  • the plurality of plate-like cooling fins 34 are formed in the same direction.
  • the orbiting scroll 30 includes an orbiting plate 35 fixed to the tip end side of the cooling fin 34.
  • the pivoting plate 35 is provided with a boss 36 which receives and secures the bearing 37 at its central portion.
  • a bearing 37 held by the boss 36 supports the eccentric shaft 53 of the drive shaft 50.
  • the turning plate 35 is provided with three bosses 38 for housing the first element 41 of the rotation preventing mechanism 40 at equal intervals in the circumferential direction, as shown in FIG.
  • the anti-rotation mechanism 40 is a pin-crank type anti-rotation mechanism and includes a first element 41 and a second element 45.
  • the scroll compressor 1 is provided with three anti-rotation mechanisms 40.
  • the first element 41 includes a bearing (first bearing) 42.
  • the bearing 42 is, for example, a ball bearing provided with an inner ring, an outer ring, and a spherical rolling element provided between the inner ring and the outer ring.
  • a crank pin (first pin) 43 is fitted to the inner ring of the bearing 42, and the first element 41 is configured together with the bearing 42.
  • the first element 41 is housed inside a boss 38 of the pivot plate 35, which boss 38 functions as a bearing housing for the bearing 42.
  • an elastic member such as an O-ring can be provided between the bearing 42 and the crankpin 43 or on the outer periphery of the bearing 42.
  • the second element 45 has the same configuration as the first element 41, and includes a bearing (second bearing) 46 and a crank pin (second pin) 47 inserted into the inner ring of the bearing 46 There is.
  • the second element 45 is accommodated and held in the accommodation chamber 11 c of the housing 10.
  • crankpin 43 of the first element 41 and the crankpin 47 of the second element 45 are integrally connected via an eccentric shaft 44.
  • the crankpin 43, the crankpin 47 and the eccentric shaft 44 are an integral crankshaft Configure
  • the boss 38 has an inner wall 38a, which regulates the amount and direction in which the bearing 42 is displaced.
  • the opening of the inner wall 38 a has an elongated diameter DL having a major axis DL in the radial direction of the revolving plate 35 which is a part of the revolving scroll 30 and a minor axis DS in the circumferential direction of the revolving plate 35 ing.
  • the outer shape of the bearing 42 is a true circle (diameter D). Therefore, assuming that the center of the region surrounded by the inner wall 38a coincides with the center of the bearing 37 as shown in FIG.
  • ⁇ r> ⁇ the boss 38 and the bearing 42 have the anisotropy that the displacement amount of the bearing 42 (crank pin 47) permitted is large in the radial direction of the turning plate 35 and small in the circumferential direction of the turning plate 35.
  • the drive shaft 50 transmits the rotational drive force of a drive source (not shown), such as an electric motor, to the orbiting scroll 30.
  • a drive source such as an electric motor
  • the drive shaft 50 is provided at one end with a connection end 51 connected to a drive source, and is provided at the other end with an eccentric shaft 53 held by a bearing 37 held by the pivot plate 35. It is done.
  • the drive shaft 50 is rotatably supported by the housing 10 by two bearings of a main bearing 54 and a sub bearing 55.
  • the main bearing 54 supports the drive shaft 50 near the eccentric shaft 53
  • the auxiliary bearing 55 supports the drive shaft 50 near the connection end 51.
  • the displacement allowance ⁇ in the circumferential direction is smaller than the displacement allowance ⁇ r in the radial direction, the amount of displacement of the bearing 42 in the circumferential direction can be reduced. Therefore, twisting of the orbiting scroll 30 with respect to the fixed scroll 20 can be suppressed.
  • the scroll compressor 1 is a 3D type compressor and fluid is compressed not only in the circumferential direction but also in the height direction, a high compression ratio can be obtained.
  • the fixed scroll 20 includes the low step 21a and the high step 21b, and as shown in FIG. 4A, the tip (tooth tip) of the wrap 22 and the end plate Steps 29a and 29b are provided at each of the connection parts (tooth bottoms) with the joint 21.
  • steps 39a and 39b are similarly provided on the tip and bottom of the lap 32 for the orbiting scroll 30 as well.
  • the steps 29a and 29b of the fixed scroll 20 and the steps 39a and 39b of the orbiting scroll 30 do not interfere with each other in a normal state.
  • the contact between the steps in the 3D type scroll compressor 1 is avoided by suppressing the amount of displacement of the bearing 42 in the circumferential direction and suppressing the displacement of the orbiting scroll 30 in the circumferential direction. it can.
  • FIGS. 5 (a) to 5 (c) The basic configuration of the scroll compressor according to the second embodiment is the same as that of the scroll compressor 1 of the first embodiment, and therefore, the support structure of the bearing 42 in the boss 38 which is the difference will be described below.
  • the inner wall 38a forms a true circle
  • the bearing 42 has a true outer shape.
  • a ring-shaped elastic member 48 is fitted on the outer periphery of the bearing 42.
  • the elastic member 48, the inner peripheral shape is corresponding to the outer shape of the bearing 42 is formed into a true circle
  • the outer periphery is formed in an oval having a major axis A L and a minor axis As. That is, the elastic member 48 is formed to have a thickness t ⁇ in the major axis A L direction larger than a thickness tr in the minor axis As direction.
  • the elastic member 48, minor As is along the radial direction, and, as the major axis A L is along the circumferential direction, are fitted on the outer periphery of the bearing 42.
  • the diameter of the inner wall 38 a is D 0
  • the diameter D 0 long diameter A L > short diameter
  • the bearing 42 crank pin 43
  • the bearing 42 is allowed to displace in the radial direction by an amount corresponding to the clearance (2 ⁇ ⁇ r).
  • the bearing 42 in the circumferential direction, although the bearing 42 can be displaced, it is limited to the range of the amount that the elastic member 48 compresses, and this displacement allowance is smaller than the displacement allowance in the radial direction (2 ⁇ ⁇ r).
  • the bearing 42 absorbs the displacement in the radial direction, while the circumferential direction is Since the amount of displacement can be reduced, twisting of the orbiting scroll 30 with respect to the fixed scroll 20 can be suppressed.
  • the orbiting scroll 30 is produced by, for example, casting, the surface accuracy of the inner wall 38a is insufficient, and machining is required.
  • the circularity as in the second embodiment It is sufficient to move the tool in the axial direction. Therefore, in the second embodiment, the boss 38 is easier to process than in the first embodiment.
  • FIGS. 6 (a) to 6 (c) The basic configuration of the scroll compressor according to the third embodiment is the same as that of the scroll compressor according to the second embodiment, and the inner wall 38a of the boss 38 has a perfect circle. Therefore, the following description focuses on the elastic member 49 which is the difference from the second embodiment.
  • the elastic member 49 of the third embodiment comprises four arc-shaped segments 49a, 49b, 49c and 49d.
  • the segments 49a, 49b, 49c and 49d are equally spaced between the bearing 42 and the inner wall 38a.
  • the segments 49a, 49b, 49c and 49d are all made of an elastic material and have the same shape and size, but the segments 49a, 49b and the segments 49c, 49d are different in elastic modulus of the material to be formed. Do. That is, the segments 49a and 49b are composed of the same material M1, the elastic modulus of the material is E1, the segments 49c and 49d are composed of the same material M2, and the elastic modulus of the material is E2. However, the elastic coefficient E1 is larger than the elastic coefficient E2 (E1> E2).
  • the large segments 49a and 49b of elastic modulus E1 are arranged along the circumferential direction, and the small segments 49c and 49d of elastic modulus E2 are arranged along the radial direction. Therefore, the bearing 42 whose circumference is constrained by the elastic members 49 (segments 49a, 49b, 49c and 49d) is easy to displace in the radial direction, and is difficult to displace in the circumferential direction in comparison with this.
  • the displacement allowable amount ⁇ r in the radial direction is larger than the displacement allowable amount ⁇ in the circumferential direction.
  • the scroll compressor 1 according to the third embodiment also has the elastic members 49 divided into the segments 49a, 49b, 49c and 49d, in addition to the same effects as in the second embodiment. Therefore, compared with the ring-shaped elastic member 48, it is easy to mount around the bearing 42. Further, since the thickness of the segments 49a, 49b, 49c and 49d is constant, the manufacturing of the elastic member 49 is easy.
  • the present invention of making the displacement allowance ⁇ r larger than the displacement allowance ⁇ is applied to all of the three anti-rotation mechanisms 40 uniformly arranged in the circumferential direction of the orbiting scroll 30, at least one anti-rotation mechanism The present invention may be applied to
  • the displacement tolerance amount ⁇ r is made larger than the displacement tolerance amount ⁇ by making the opening shape of the inner wall 38a an oval, but while making the opening shape of the inner wall 38a a perfect circle, Can be made larger than the displacement allowance .delta..theta.
  • the displacement tolerance ⁇ r is made larger than the displacement tolerance amount ⁇ by making the opening shape of the inner wall 38a an oval, but while making the opening shape of the inner wall 38a a perfect circle, Can be made larger than the displacement allowance .delta..theta.
  • another member such as the above in the circumferential direction of the inner wall 38a.
  • the opening shape of the inner wall 38a is elongated.
  • the displacement tolerance ⁇ r can be made larger than the displacement tolerance ⁇ , it is not necessary to be limited to the oval. , Rectangular opening shape. The same applies to the elastic member 48 of the second embodiment.
  • the elastic members 48 and 49 are interposed between the outer ring and the inner wall 38a of the bearing 42.
  • the elastic member is the inner ring of the bearing 42 and the crankpins 43 and 47. Can also be intervened.
  • the elastic member 48 of the second embodiment can also be divided into a plurality of segments as in the third embodiment. In this case, each segment has the same thickness, but the number of segments to be interposed in the circumferential direction may be larger than that in the radial direction. For example, if one segment is interposed in the radial direction, but two segments are interposed in the circumferential direction, the displacement allowance ⁇ r can be made larger than the displacement allowance ⁇ .
  • the elastic member 49 is made of a composite material in which two types of materials having different elastic coefficients are integrally formed. It can also be done.
  • the scroll compressor 1 is merely an example, and the present invention can be widely applied to a scroll compressor using a pin crank type anti-rotation mechanism.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2015/000060 2014-02-17 2015-01-08 スクロール圧縮機 WO2015122111A1 (ja)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014027426A JP6335542B2 (ja) 2014-02-17 2014-02-17 スクロール圧縮機
JP2014-027426 2014-02-17

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WO2015122111A1 true WO2015122111A1 (ja) 2015-08-20

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JP (1) JP6335542B2 (enrdf_load_stackoverflow)
WO (1) WO2015122111A1 (enrdf_load_stackoverflow)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109185130A (zh) * 2018-10-26 2019-01-11 珠海格力节能环保制冷技术研究中心有限公司 一种用于涡旋空气压缩机的泵头及涡旋空气压缩机
CN111927770A (zh) * 2020-07-27 2020-11-13 周岩 一种立体气体涡旋压缩结构

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